Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State

*Vladimir A. Pukhliy*

#### **Abstract**

An analytical approach is described to determine the resource of structural elements of hydropower, the nuclear industry, etc., under difficult stress conditions when exposed to a corrosive environment with certain parameters (degree of chemical activity, temperature, humidity, flow rate, etc.). The initial-boundary problem for structural elements (bimetallic pipelines, centrifugal pumps) is considered with a decrease in the thickness of the element due to the influence of a corrosive environment. In this case, the effect of a corrosive medium on an element is described by a differential equation with certain initial conditions. Equations describing the stress-strain state of an element are added to this equation. As the first object, the corrosion wear of bimetallic pipelines of nuclear energy is considered. The solution to the problem is to integrate the ordinary differential equation. The criterion for terminating the step-by-step process in time is the condition

*σ* max min *ij* ≤½ � *σ<sup>T</sup>* , where *σ<sup>T</sup>* is the yield strength of the material of the structural

 element. As the second object, the corrosion wear of the working blades of centrifugal pumps is considered. The stress-strain state of the blade is described by a system of partial differential equations of the 12th order, to the solution of which the method of integral relations by Dorodnitsyn is applied. At the next stage, the system of ordinary differential equations is integrated by the modified method of successive approximations developed by Professor V.A. Pukhliy. At each stage, the corrosion equation is attached to the solution of this problem. For bimetallic pipelines, a specific example of calculation according to the described algorithm has been implemented.

**Keywords:** general corrosion, pipelines of hydropower and nuclear energy, corrosion cracking, two-layer shells, initial-boundary value problem, centrifugal pumps, modified method of successive approximation

#### **1. Introduction**

In a number of industries, in particular in the chemical industry, axial and radial turbomachines (compressors, superchargers, gas turbine installations, pumps)

operate under aggressive environments, as a result of which rotor blades and disks are subject to corrosion wear.

Pipelines of hydropower are subject to corrosion wear, as a result of which their service life is significantly reduced. The problem of corrosion is especially acute in nuclear energy. Pipelines are made of low-alloy pearlite-grade carbon steel with stainless steel cladding on the inner surface. We also note that all parts and assemblies of the main circulation pumps in contact with the coolant, industrial cooling water, and locking water are made of special steels that are resistant to corrosion.

The coolant of the first circuit of a nuclear reactor is not just pure water, but water with boric acid dissolved in it (H3BO3), which contributes to significant corrosion of metal in pipelines. Steam generators of nuclear plants are made of pipes clad with anticorrosive austenitic surfacing.

It should be emphasized that the influence of the stress-strain state on the rate of corrosion and erosion wear also becomes important. For example, a strain of 1% increases the rate of corrosion of silicon iron in a 0.01% solution of sulfuric acid by 53% compared with undeformed metal [1].

Stress corrosion cracking of metals was previously studied. This phenomenon takes place at certain critical (threshold) values of tension determined by the acting stresses and potential energy. Stresses less than critical have an effect on general corrosion without causing cracking.

The impellers of radial and axial turbomachines subjected to corrosion are usually thin-walled plates and shells. The problem of the durability of the elements of the impellers of turbomachines is the problem of the durability of plates and shells of a variable thickness over time, under the influence of an aggressive environment that has certain parameters (degree of chemical activity, temperature, flow rate, etc.), and the stress-strain state.

In the present paper, an analytical approach to determining the resource of structural elements of nuclear power units based on the theory of bimetallic shells, taking into account the stress-strain state and corrosion wear of the elements, is

**Corrosion equation wear The law of the effect of stress on corrosion rate**

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

*dh dt*

*dh dt*

*dh dt*

*dh dt*

Consider a cylindrical bimetallic shell when exposed to a corrosive environment [4]. Such tasks are very important in relation to the design of pipelines of nuclear

The rate of change of thickness at a given point in the shell is taken in the form:

where x, y are the normal coordinates of the middle surface of the shell; T is the

Note that F is a known function whose form is determined from experiment and

We study the effect of the stress state on general corrosion under the assumption

Here *σij* is the stress intensity on the surface of the bimetallic shell; *α* and *k* are finite coefficients; and *φ*ð Þ*t* is a dimensionless function of time. As a rule, in most

It is necessary to add the equations of the theory of bimetallic shells to Eq. (1) or (3). As a result, we obtain an unrelated problem of the theory of shells, in view of

practical cases *φ*ð Þ*t* it is a constant or monotonically decreasing function.

temperature; and σ is the function connecting the rate of change of the shell

that the corrosion rate is a linear function of the stress intensity. The equations of corrosion wear are written as follows:

*dt* <sup>¼</sup> *F t*ð Þ , *<sup>T</sup>*, *<sup>σ</sup>* , 0 <sup>≤</sup>*t*≤*tk*, *<sup>h</sup>*<sup>&</sup>gt; <sup>0</sup>*:* (1)

*dt* ¼ �*αφ*ð Þ*<sup>t</sup>* <sup>1</sup> <sup>þ</sup> *<sup>k</sup>σij* , 0 <sup>≤</sup>*t*<sup>≤</sup> *tk*, *<sup>h</sup>*>0*:* (3)

*h x*ð Þ¼ , *y*, 0 *h*0ð Þ *x*, *y* , (2)

presented.

*dh*

*dh*

*dh*

*dh dt* ¼ *α* � *βe*

**Table 1.**

*Corrosion wear models.*

*dt* ¼ *φ*ð Þ*t* ð Þ 1 þ *kσ*

*dt* <sup>¼</sup> *<sup>φ</sup>*ð Þ*<sup>t</sup> <sup>c</sup>ασ=RT*

*dt* ¼ *α* þ *β σ*ð Þ � *σ*<sup>0</sup> *ε*

�*γσ*

power plants (corrosion cracking).

with the initial condition:

*tk* is the final point in time.

**99**

*dh*

thickness with the stress state at a surface point.

*dh*

One of the first works in this direction was an article by Kornishin [2], in which a joint solution of the corrosion equation is considered, which is a linear dependence of the corrosion rate on stress and equations describing the stress-strain state of a shell of variable thickness. The system of joint equations describing the behavior of the shell in a corrosive medium is then solved in finite differences according to a two-layer explicit scheme with a time step.

To date, there are a number of semi-empirical models that approximate corrosion wear taking into account the stress state. In T**able 1**, a number of models used in the calculations are given [3].

**Table 1** indicates: h is the depth of the wear layer; t is the time; σ and ε are stress and strain; T is the temperature; k, α, β, and γ are constants; and φ (t) are some functions.

The issues of corrosion wear of centrifugal fan elements were investigated in a number of works by Pukhliy and Semenenko [1, 4, 5].

#### **2. Corrosion cracking of bimetallic pipelines**

Bimetallic structures are widely used in modern technology, in particular, in the manufacture of bimetallic elements in nuclear energy. These are, first of all, bimetallic pipelines, bends, etc. These elements are characterized by high strength, heat resistance, and corrosion resistance.

The structural elements of nuclear power units operate under complex loading conditions, in particular, under conditions of exposure to aggressive environments. In this regard, the determination of the time to destruction of structural elements (resource) is the most important in the study of corrosion wear of elements that are in a complex stress-strain state [6–8].

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

operate under aggressive environments, as a result of which rotor blades and disks

Pipelines of hydropower are subject to corrosion wear, as a result of which their service life is significantly reduced. The problem of corrosion is especially acute in nuclear energy. Pipelines are made of low-alloy pearlite-grade carbon steel with stainless steel cladding on the inner surface. We also note that all parts and assemblies of the main circulation pumps in contact with the coolant, industrial cooling water, and locking water are made of special steels that are resistant to corrosion. The coolant of the first circuit of a nuclear reactor is not just pure water, but water with boric acid dissolved in it (H3BO3), which contributes to significant corrosion of metal in pipelines. Steam generators of nuclear plants are made of pipes

It should be emphasized that the influence of the stress-strain state on the rate of corrosion and erosion wear also becomes important. For example, a strain of 1% increases the rate of corrosion of silicon iron in a 0.01% solution of sulfuric acid by

Stress corrosion cracking of metals was previously studied. This phenomenon takes place at certain critical (threshold) values of tension determined by the acting stresses and potential energy. Stresses less than critical have an effect on general

The impellers of radial and axial turbomachines subjected to corrosion are usually thin-walled plates and shells. The problem of the durability of the elements of the impellers of turbomachines is the problem of the durability of plates and shells of a variable thickness over time, under the influence of an aggressive environment that has certain parameters (degree of chemical activity, temperature, flow rate,

One of the first works in this direction was an article by Kornishin [2], in which a joint solution of the corrosion equation is considered, which is a linear dependence of the corrosion rate on stress and equations describing the stress-strain state of a shell of variable thickness. The system of joint equations describing the behavior of the shell in a corrosive medium is then solved in finite differences according to a

To date, there are a number of semi-empirical models that approximate corrosion wear taking into account the stress state. In T**able 1**, a number of models used

**Table 1** indicates: h is the depth of the wear layer; t is the time; σ and ε are stress and strain; T is the temperature; k, α, β, and γ are constants; and φ (t) are some

The issues of corrosion wear of centrifugal fan elements were investigated in a

Bimetallic structures are widely used in modern technology, in particular, in the manufacture of bimetallic elements in nuclear energy. These are, first of all, bimetallic pipelines, bends, etc. These elements are characterized by high strength, heat

The structural elements of nuclear power units operate under complex loading conditions, in particular, under conditions of exposure to aggressive environments. In this regard, the determination of the time to destruction of structural elements (resource) is the most important in the study of corrosion wear of elements that are

are subject to corrosion wear.

*Corrosion*

clad with anticorrosive austenitic surfacing.

53% compared with undeformed metal [1].

corrosion without causing cracking.

etc.), and the stress-strain state.

in the calculations are given [3].

resistance, and corrosion resistance.

in a complex stress-strain state [6–8].

functions.

**98**

two-layer explicit scheme with a time step.

number of works by Pukhliy and Semenenko [1, 4, 5].

**2. Corrosion cracking of bimetallic pipelines**

*Corrosion wear models.*

In the present paper, an analytical approach to determining the resource of structural elements of nuclear power units based on the theory of bimetallic shells, taking into account the stress-strain state and corrosion wear of the elements, is presented.

Consider a cylindrical bimetallic shell when exposed to a corrosive environment [4]. Such tasks are very important in relation to the design of pipelines of nuclear power plants (corrosion cracking).

The rate of change of thickness at a given point in the shell is taken in the form:

$$\frac{dh}{dt} = F(t, T, \sigma), \mathbf{0} \le t \le t\_k, h > \mathbf{0}. \tag{1}$$

with the initial condition:

$$h(\mathbf{x}, \mathbf{y}, \mathbf{0}) = h\_0(\mathbf{x}, \mathbf{y}), \tag{2}$$

where x, y are the normal coordinates of the middle surface of the shell; T is the temperature; and σ is the function connecting the rate of change of the shell thickness with the stress state at a surface point.

Note that F is a known function whose form is determined from experiment and *tk* is the final point in time.

We study the effect of the stress state on general corrosion under the assumption that the corrosion rate is a linear function of the stress intensity.

The equations of corrosion wear are written as follows:

$$\frac{dh}{dt} = -a\rho(t)\left(\mathbf{1} + k\sigma\_{\vec{\eta}}\right), \mathbf{0} \le t \le t\_k, h > \mathbf{0}.\tag{3}$$

Here *σij* is the stress intensity on the surface of the bimetallic shell; *α* and *k* are finite coefficients; and *φ*ð Þ*t* is a dimensionless function of time. As a rule, in most practical cases *φ*ð Þ*t* it is a constant or monotonically decreasing function.

It is necessary to add the equations of the theory of bimetallic shells to Eq. (1) or (3). As a result, we obtain an unrelated problem of the theory of shells, in view of

which it is possible to apply a finite-difference approximation in time to the solution of Eq. (3).

Thus, the algorithm for solving the initial-boundary-value problem is reduced to the joint solution of Eq. (3) under the initial conditions in Eq. (2) and the system of equations for bimetallic shells, in the general case of variable thickness under the corresponding boundary conditions. Moreover, at each time step from Eq. (3), we obtain numerical values of the thickness of the structural element, which are then used to construct spline functions [9]. Then the system of equations of bimetallic shells is solved, from the solution of which the values of *σij* are determined.

The criterion for terminating the step-by-step process is the following condition:

$$\left| \max\_{\sigma\_{\vec{\eta}}} \right| \quad \begin{array}{l} \max \\ \min \\ \leq [\sigma\_T], \\ \text{max} \end{array} \right| \leq [\sigma\_T],$$

where *σ<sup>T</sup>* is the yield strength of the material of the structural element. The resource of structural elements of nuclear power units as a whole is

determined by the summation of time steps. We obtain the equilibrium equation of the bimetallic shell on the basis of the Lagrange variational principle:

$$
\delta\Pi = \delta\Pi\_1 + \delta\Pi\_2 = \mathbf{0}.\tag{4}
$$

The movement of u and v in are the direction of the tangents to *α*<sup>1</sup> and *α*<sup>2</sup> and w

Deformations of the junction surface are determined by relative elongations *ε*<sup>1</sup> and *ε*<sup>2</sup> in both the *α*<sup>1</sup> and *α*<sup>2</sup> directions, and by a shift *γ*12�a change in the angle between the tangents to the lines *α*<sup>1</sup> and *α*<sup>2</sup> (before deformation *π=*2, after *<sup>π</sup>*

*p*1, *p*2, *p*<sup>3</sup> the projection of external surface forces, referred to the unit of the junction surface, on the direction of the tangents to the lines of curvature *α*<sup>1</sup> and *α*<sup>2</sup>

<sup>2</sup> the same for section*α*<sup>2</sup> ¼ *const*. Then the variation of the potential of external forces is equal to:

<sup>2</sup> *<sup>δ</sup><sup>v</sup>* <sup>þ</sup> *<sup>T</sup><sup>α</sup>*<sup>1</sup>

*<sup>p</sup>*1*δ<sup>u</sup>* <sup>þ</sup> *<sup>p</sup>*2*δ<sup>v</sup>* <sup>þ</sup> *<sup>p</sup>*3*δ<sup>w</sup>* � �*A*1*A*2*dα*1*dα*<sup>2</sup> �

*N<sup>α</sup>*<sup>2</sup>

*a*ð2

*a*1

Substituting Eqs. (6) and (7) in Eq. (4) we obtain:

*N*1*δε*<sup>1</sup> þ *N*2*δε*<sup>2</sup> � *M*1*δχ*<sup>1</sup> � *M*2*δχ*<sup>2</sup> þ *Tδγ*<sup>12</sup> � *Hδχ*<sup>12</sup> ð Þ*A*1*A*2*dα*1*dα*<sup>2</sup> (6)

<sup>1</sup> the normal, shear, shear forces, and bending moment for the

*b* ð2

*N<sup>α</sup>*<sup>1</sup> <sup>1</sup> *<sup>δ</sup><sup>u</sup>* � <sup>þ</sup> *<sup>T</sup><sup>α</sup>*<sup>1</sup>

<sup>2</sup> *<sup>δ</sup>v*<sup>2</sup> <sup>þ</sup> *<sup>Q</sup><sup>α</sup>*<sup>2</sup> <sup>2</sup> *<sup>δ</sup><sup>w</sup>* � �*A*1*dα*1*:* (7)

<sup>1</sup> *<sup>δ</sup><sup>v</sup>* � *<sup>M</sup><sup>α</sup>*<sup>1</sup>

<sup>1</sup> *δv*<sup>1</sup>

*b*1

<sup>2</sup> *<sup>δ</sup><sup>u</sup>* � *<sup>M</sup><sup>α</sup>*<sup>2</sup>

<sup>2</sup> � *γ*12).

in the direction of the normal to the junction surface.

*System of curvilinear coordinates on an undeformed junction surface.*

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

Eq. (5) can be represented as follows:

*δ*Π<sup>1</sup> ¼

**Figure 1.**

*N<sup>α</sup>*<sup>1</sup> <sup>1</sup> , *<sup>T</sup><sup>α</sup>*<sup>1</sup> <sup>1</sup> , *<sup>Q</sup><sup>α</sup>*<sup>1</sup>

*δ*Π<sup>2</sup> ¼ �

**101**

*a*ð2

*b* ð2

*b*1

and normal to the junction surface;

<sup>1</sup> , *<sup>M</sup><sup>α</sup>*<sup>1</sup>

<sup>2</sup> , *<sup>M</sup><sup>α</sup>*<sup>2</sup>

*A*2*dα*<sup>2</sup> �

*a*1

Denote by:

section*α*<sup>1</sup> ¼ *const*; *N<sup>α</sup>*<sup>2</sup> <sup>2</sup> , *<sup>T</sup><sup>α</sup>*<sup>2</sup> <sup>2</sup> , *<sup>Q</sup><sup>α</sup>*<sup>2</sup>

*a*ð2

*b* ð2

*b*1

*a*1

<sup>þ</sup> *<sup>Q</sup><sup>α</sup>*<sup>1</sup> <sup>1</sup> *δw* �

Here *δ*Π<sup>1</sup> is a variation of the potential energy of shell deformation; *δ*Π<sup>2</sup> is a variation of the potential of external forces, equal to the variations of the work of external forces, taken with the opposite sign.

We write an expression for the variation of potential energy:

$$
\delta\Pi\_1 = \int\_{a\_1}^{a\_2} \int\_{b\_1} \delta a\_0 A\_1 A\_2 da\_1 da\_2 = \int\_{a\_1}^{a\_2} \int\_{b\_1} \delta a\_0 dS\_1 dS\_2,\tag{5}
$$

where *a*<sup>0</sup> is the potential energy of deformation of a unit surface of the shell.

Integration extends to the entire surface of the junction (**Figure 1**): from *α*<sup>1</sup> ¼ *a*<sup>1</sup> to *α*<sup>1</sup> ¼ *a*<sup>2</sup> and from *α*<sup>2</sup> ¼ *b*<sup>1</sup> to *α*<sup>2</sup> ¼ *b*2.

$$
\begin{split}
\delta\mathfrak{a}\_{0} &= \int\_{0}^{\delta\_{1}} \left[ \sigma\_{1}^{(1)} \cdot \delta\varepsilon\_{1}^{(1)} + \sigma\_{2}^{(1)} \delta\varepsilon\_{2}^{(1)} + \tau\_{12}^{(1)} \delta\gamma\_{12}^{(1)} \right] \left( 1 - \frac{z}{R\_{1}} \right) \left( 1 - \frac{z}{R\_{2}} \right) dz \\ &\quad + \int\_{-\delta\_{1}}^{0} \left[ \sigma\_{1}^{(2)} \delta\varepsilon\_{1}^{(2)} + \sigma\_{2}^{(2)} \cdot \delta\varepsilon\_{2}^{(2)} + \tau\_{12}^{(2)} \delta\gamma\_{12}^{(2)} \right] \left( 1 - \frac{z}{R\_{1}} \right) \left( 1 - \frac{z}{R\_{2}} \right) dz
\end{split}
$$

In the analysis, the following assumptions are used (**Figure 1**).

The curvilinear coordinate system coincides with the lines of the main curvatures. This coordinate system is a Gaussian coordinate system, it is orthogonal.

The position of the point that does not belong to the junction surface determines the coordinates of the z-distance normal to the point from the junction surface (+ if it is directed along the internal normal to the junction surface).

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

**Figure 1.** *System of curvilinear coordinates on an undeformed junction surface.*

The movement of u and v in are the direction of the tangents to *α*<sup>1</sup> and *α*<sup>2</sup> and w in the direction of the normal to the junction surface.

Deformations of the junction surface are determined by relative elongations *ε*<sup>1</sup> and *ε*<sup>2</sup> in both the *α*<sup>1</sup> and *α*<sup>2</sup> directions, and by a shift *γ*12�a change in the angle between the tangents to the lines *α*<sup>1</sup> and *α*<sup>2</sup> (before deformation *π=*2, after *<sup>π</sup>* <sup>2</sup> � *γ*12).

Eq. (5) can be represented as follows:

$$\delta \Pi\_1 = \int\_{a\_1}^{a\_2} \int\_{b\_1} (N\_1 \delta e\_1 + N\_2 \delta e\_2 - M\_1 \delta \chi\_1 - M\_2 \delta \chi\_2 + T \delta \gamma\_{12} - H \delta \chi\_{12}) A\_1 A\_2 d\alpha\_1 da\_2 \tag{6}$$

Denote by:

which it is possible to apply a finite-difference approximation in time to the solution

Thus, the algorithm for solving the initial-boundary-value problem is reduced

The criterion for terminating the step-by-step process is the following condition:

≤½ � *σ<sup>T</sup>* ,

*δ*Π ¼ *δ*Π<sup>1</sup> þ *δ*Π<sup>2</sup> ¼ 0*:* (4)

*δa*0*dS*1*dS*2, (5)

<sup>1</sup> � *<sup>z</sup> R*2 � �

*dz*

*dz*

<sup>1</sup> � *<sup>z</sup> R*2 � �

*a*ð2

*b* ð2

*b*1

<sup>1</sup> � *<sup>z</sup> R*1 � �

> <sup>1</sup> � *<sup>z</sup> R*1 � �

*a*1

� � � � � � � �

to the joint solution of Eq. (3) under the initial conditions in Eq. (2) and the system of equations for bimetallic shells, in the general case of variable thickness under the corresponding boundary conditions. Moreover, at each time step from Eq. (3), we obtain numerical values of the thickness of the structural element, which are then used to construct spline functions [9]. Then the system of equations

of bimetallic shells is solved, from the solution of which the values of *σij* are

max min *ij*

where *σ<sup>T</sup>* is the yield strength of the material of the structural element. The resource of structural elements of nuclear power units as a whole is

We obtain the equilibrium equation of the bimetallic shell on the basis of the

Here *δ*Π<sup>1</sup> is a variation of the potential energy of shell deformation; *δ*Π<sup>2</sup> is a variation of the potential of external forces, equal to the variations of the work of

*δa*0*A*1*A*2*dα*1*dα*<sup>2</sup> ¼

where *a*<sup>0</sup> is the potential energy of deformation of a unit surface of the shell. Integration extends to the entire surface of the junction (**Figure 1**): from *α*<sup>1</sup> ¼ *a*<sup>1</sup>

> <sup>2</sup> þ *τ* ð Þ2 <sup>12</sup> *δγ*ð Þ<sup>2</sup> 12

The curvilinear coordinate system coincides with the lines of the main curvatures. This coordinate system is a Gaussian coordinate system, it is orthogonal.

The position of the point that does not belong to the junction surface determines the coordinates of the z-distance normal to the point from the junction surface (+ if

We write an expression for the variation of potential energy:

*σ*

� � � � � � � �

determined by the summation of time steps.

external forces, taken with the opposite sign.

*δ*Π<sup>1</sup> ¼

to *α*<sup>1</sup> ¼ *a*<sup>2</sup> and from *α*<sup>2</sup> ¼ *b*<sup>1</sup> to *α*<sup>2</sup> ¼ *b*2.

*σ*ð Þ<sup>1</sup> <sup>1</sup> � *δε*ð Þ<sup>1</sup>

*δa*<sup>0</sup> ¼

**100**

*δ* ð1

0

þ ð 0

�*δ*<sup>2</sup>

*σ*ð Þ<sup>2</sup> <sup>1</sup> *δε*ð Þ<sup>2</sup>

*a*ð2

*b* ð2

*b*1

<sup>1</sup> <sup>þ</sup> *<sup>σ</sup>*ð Þ<sup>1</sup>

<sup>2</sup> *δε*ð Þ<sup>1</sup> <sup>2</sup> þ *τ* ð Þ1 <sup>12</sup> *δγ*ð Þ<sup>1</sup> 12

<sup>2</sup> � *δε*ð Þ<sup>2</sup>

h i

In the analysis, the following assumptions are used (**Figure 1**).

h i

<sup>1</sup> <sup>þ</sup> *<sup>σ</sup>*ð Þ<sup>2</sup>

it is directed along the internal normal to the junction surface).

*a*1

Lagrange variational principle:

of Eq. (3).

*Corrosion*

determined.

*p*1, *p*2, *p*<sup>3</sup> the projection of external surface forces, referred to the unit of the junction surface, on the direction of the tangents to the lines of curvature *α*<sup>1</sup> and *α*<sup>2</sup> and normal to the junction surface;

*N<sup>α</sup>*<sup>1</sup> <sup>1</sup> , *<sup>T</sup><sup>α</sup>*<sup>1</sup> <sup>1</sup> , *<sup>Q</sup><sup>α</sup>*<sup>1</sup> <sup>1</sup> , *<sup>M</sup><sup>α</sup>*<sup>1</sup> <sup>1</sup> the normal, shear, shear forces, and bending moment for the section*α*<sup>1</sup> ¼ *const*;

*N<sup>α</sup>*<sup>2</sup> <sup>2</sup> , *<sup>T</sup><sup>α</sup>*<sup>2</sup> <sup>2</sup> , *<sup>Q</sup><sup>α</sup>*<sup>2</sup> <sup>2</sup> , *<sup>M</sup><sup>α</sup>*<sup>2</sup> <sup>2</sup> the same for section*α*<sup>2</sup> ¼ *const*.

Then the variation of the potential of external forces is equal to:

$$
\delta \Pi\_2 = -\int\_{a\_1}^{a\_1} \int (p\_1 \delta u + p\_2 \delta v + p\_3 \delta w) A\_1 A\_2 da\_1 da\_2 - \int\_{b\_1}^{b\_2} (N\_1^{\alpha} \delta u + T\_1^{\alpha} \delta v - M\_1^{\alpha} \delta v\_1)
$$

$$
+ Q\_1^{\alpha} \delta w \Big) A\_2 da\_2 - \int\_{a\_1}^{a\_2} (N\_2^{\alpha} \delta v + T\_2^{\alpha} \delta u - M\_2^{\alpha} \delta v\_2 + Q\_2^{\alpha} \delta w) A\_1 da\_1. \tag{7}
$$

Substituting Eqs. (6) and (7) in Eq. (4) we obtain:

*Corrosion*

*δ*Π ¼� *a*ð2 *a*1 *b* ð2 *b*1 *∂N*1*A*<sup>2</sup> *∂α*<sup>1</sup> � *N*<sup>2</sup> *∂A*<sup>2</sup> *∂α*<sup>1</sup> þ *∂T*2*A*<sup>1</sup> *∂α*<sup>2</sup> þ *T*<sup>1</sup> *∂A*<sup>1</sup> *∂α*<sup>2</sup> � *<sup>A</sup>*1*A*<sup>2</sup> *R*1 *Q*<sup>1</sup> þ *A*1*A*2*p*<sup>1</sup> �� �*δu*<sup>þ</sup> þ *∂N*2*A*<sup>1</sup> *∂α*<sup>2</sup> � *N*<sup>1</sup> *∂A*<sup>1</sup> *∂α*<sup>2</sup> þ *T*<sup>2</sup> *∂A*<sup>2</sup> *∂α*<sup>1</sup> � *<sup>A</sup>*1*A*<sup>2</sup> *R*2 *Q*<sup>2</sup> þ *A*1*A*2*p*<sup>2</sup> � �*δv*<sup>þ</sup> þ *∂Q*1*A*<sup>2</sup> *∂α*<sup>1</sup> þ *∂Q*2*A*<sup>1</sup> *∂α*<sup>2</sup> þ *A*1*A*<sup>2</sup> *N*<sup>1</sup> *R*1 þ *N*<sup>2</sup> *R*2 � � þ *A*1*A*2*p*<sup>3</sup> � �*δ<sup>w</sup>* � *dα*1*dα*2þ þ *b* ð2 *b*1 *<sup>N</sup>*<sup>1</sup> � *<sup>N</sup><sup>α</sup>*<sup>1</sup> 1 � � *<sup>δ</sup><sup>u</sup>* <sup>þ</sup> *<sup>T</sup>*<sup>1</sup> � *<sup>H</sup>*<sup>1</sup> *R*2 � *<sup>T</sup><sup>α</sup>*<sup>2</sup> 1 � � *<sup>δ</sup><sup>v</sup>* � � *<sup>M</sup>*<sup>1</sup> � *<sup>M</sup><sup>α</sup>*<sup>1</sup> 1 � � *δ* 1 *A*1 *∂w ∂α*<sup>1</sup> þ *u R*1 � �þ þ *Q*<sup>1</sup> þ 1 *A*2 *∂H*<sup>1</sup> *∂α*<sup>2</sup> � *<sup>Q</sup><sup>α</sup>*<sup>1</sup> 1 � �*δ<sup>w</sup>* � *A*2*dα*<sup>2</sup> þ *a*ð2 *a*1 *<sup>T</sup>*<sup>2</sup> � *<sup>H</sup>*<sup>2</sup> *R*1 � *<sup>T</sup><sup>α</sup>*<sup>2</sup> 2 � �*δ<sup>u</sup>* � <sup>þ</sup> *<sup>N</sup>*<sup>2</sup> � *<sup>N</sup><sup>α</sup>*<sup>2</sup> 2 � � *<sup>δ</sup>v*� � *<sup>M</sup>*<sup>2</sup> � *<sup>M</sup><sup>α</sup>*<sup>2</sup> 2 � � *δ* 1 *A*2 *∂w ∂α*<sup>2</sup> þ *v R*2 � � þ *Q*<sup>2</sup> þ 1 *A*1 *∂H*<sup>2</sup> *∂α*<sup>1</sup> � *<sup>Q</sup><sup>α</sup>*<sup>2</sup> 2 � � *<sup>δ</sup><sup>w</sup>* � � f g ½ � *H*<sup>1</sup> þ *H*<sup>2</sup> *δw <sup>b</sup>*1,*a*<sup>1</sup> � �f g ½ � *H*<sup>1</sup> þ *H*<sup>2</sup> *δw <sup>b</sup>*2,*a*<sup>2</sup> þ f g ½ � *H*<sup>1</sup> þ *H*<sup>2</sup> *δw <sup>b</sup>*2,*a*<sup>2</sup> þ f g ½ � *H*<sup>1</sup> þ *H*<sup>2</sup> *δw <sup>b</sup>*1,*a*<sup>2</sup> *:* (8)

Here *Q*<sup>1</sup> and *Q*<sup>2</sup> are the transverse forces arising in the shell:

$$Q\_1 = \frac{1}{A\_1 A\_2} \left[ \frac{\partial M\_1 A\_2}{\partial a\_1} - M\_2 \frac{\partial A\_2}{\partial a\_1} + H\_1 \frac{\partial A\_2}{\partial a\_2} + \frac{\partial H\_2 A\_1}{\partial a\_2} \right];\tag{9}$$

$$Q\_2 = \frac{1}{A\_1 A\_2} \left[ \frac{\partial M\_2 A\_1}{\partial a\_2} - M\_1 \frac{\partial A\_1}{\partial a\_2} + H\_2 \frac{\partial A\_2}{\partial a\_1} + \frac{\partial H\_1 A\_2}{\partial a\_1} \right]. \tag{10}$$

From the expressions in Eqs. (9)–(10), two more equations follow:

*∂A*<sup>2</sup> *∂α*<sup>1</sup> þ

*∂A*<sup>1</sup> *∂α*<sup>2</sup> þ

*<sup>T</sup>*<sup>1</sup> � *<sup>T</sup>*<sup>2</sup> � *<sup>H</sup>*<sup>1</sup>

*∂H*2*A*<sup>1</sup> *∂α*<sup>2</sup>

*∂H*1*A*<sup>2</sup> *∂α*<sup>1</sup>

The sixth equation is an identity expressing the equality of the moments of all forces acting on the element to zero relative to the axis normal to the surface of the

> *R*1 þ *H*<sup>2</sup> *R*2 ¼ 0*:*

The second and third integrals of expression in Eq. (8) give boundary conditions

for the edges *α*<sup>1</sup> ¼ *const* and *α*<sup>2</sup> ¼ *const*, that is, for lines of principal curvatures.

þ *H*<sup>1</sup>

þ *H*<sup>2</sup>

*∂A*<sup>1</sup> *∂α*<sup>2</sup>

*∂A*<sup>2</sup> *∂α*<sup>1</sup>

� *Q*<sup>1</sup> ¼ 0;

(12)

� *Q*<sup>2</sup> ¼ 0*:*

1 *A*1*A*<sup>2</sup>

*Internal forces acting on the edge of the element.*

1 *A*1*A*<sup>2</sup>

element junction:

**Figure 2.**

**2.2 Border conditions**

**103**

*<sup>∂</sup>M*1*A*<sup>2</sup> *∂α*<sup>1</sup>

*∂M*2*A*<sup>1</sup> *∂α*<sup>2</sup>

This equation was used to obtain Eq. (11).

� *M*<sup>2</sup>

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

� *M*<sup>1</sup>

The last four terms in Eq. (8) is the work of concentrated forces along the edges of the shell *α*<sup>1</sup> ¼ *const*, *α*<sup>2</sup> ¼ *const*.

From Eq. (8), we obtain the equilibrium equation and boundary conditions.

#### **2.1 Equilibrium equations**

In the mechanics of a solid deformable body, equilibrium equations can be obtained by making up for the main vector and the main moment of all the forces acting on the element for the infinitely small element extracted from the shell under the influence of external and internal forces (**Figure 2**). Here, the equilibrium equations and boundary conditions are obtained from the variational Lagrange principle in Eq. (4).

Note that in the case of dynamics, it is necessary to apply the variational Hamilton-Ostrogradsky principle.

So, from the first integral of expression in Eq. (8), the first three equations of equilibrium follow:

$$\begin{aligned} &\frac{1}{\mathbf{A}\_{1}\mathbf{A}\_{2}}\left[\frac{\partial \mathbf{N}\_{1}\mathbf{A}\_{2}}{\partial \alpha\_{1}} - \mathbf{N}\_{2}\frac{\partial \mathbf{A}\_{2}}{\partial \alpha\_{1}} + \frac{\partial \mathbf{T}\_{2}\mathbf{A}\_{1}}{\partial \alpha\_{2}} + \mathbf{T}\_{1}\frac{\partial \mathbf{A}\_{1}}{\partial \alpha\_{2}}\right] - \frac{\mathbf{Q}\_{1}}{\mathbf{R}\_{1}} + \mathbf{p}\_{1} = \mathbf{0};\\ &\frac{1}{\mathbf{A}\_{1}\mathbf{A}\_{2}}\left[\frac{\partial \mathbf{T}\_{1}\mathbf{A}\_{2}}{\partial \alpha\_{1}} - \mathbf{N}\_{1}\frac{\partial \mathbf{A}\_{1}}{\partial \alpha\_{2}} + \frac{\partial \mathbf{N}\_{2}\mathbf{A}\_{1}}{\partial \alpha\_{2}} + \mathbf{T}\_{2}\frac{\partial \mathbf{A}\_{2}}{\partial \alpha\_{1}}\right] - \frac{\mathbf{Q}\_{2}}{\mathbf{R}\_{2}} + \mathbf{p}\_{2} = \mathbf{0};\\ &\frac{1}{\mathbf{A}\_{1}\mathbf{A}\_{2}}\left[\frac{\partial \mathbf{Q}\_{1}\mathbf{A}\_{2}}{\partial \alpha\_{1}} + \frac{\partial \mathbf{Q}\_{2}\mathbf{A}\_{1}}{\partial \alpha\_{2}}\right] - \frac{\mathbf{N}\_{1}}{\mathbf{R}\_{1}} + \frac{\mathbf{N}\_{2}}{\mathbf{R}\_{2}} + \mathbf{p}\_{3} = \mathbf{0}.\end{aligned} \tag{11}$$

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

**Figure 2.** *Internal forces acting on the edge of the element.*

From the expressions in Eqs. (9)–(10), two more equations follow:

$$\begin{split} \frac{1}{A\_1 A\_2} \left[ \frac{\partial M\_1 A\_2}{\partial \alpha\_1} - M\_2 \frac{\partial A\_2}{\partial \alpha\_1} + \frac{\partial H\_2 A\_1}{\partial \alpha\_2} + H\_1 \frac{\partial A\_1}{\partial \alpha\_2} \right] - Q\_1 &= 0; \\ \frac{1}{A\_1 A\_2} \left[ \frac{\partial M\_2 A\_1}{\partial \alpha\_2} - M\_1 \frac{\partial A\_1}{\partial \alpha\_2} + \frac{\partial H\_1 A\_2}{\partial \alpha\_1} + H\_2 \frac{\partial A\_2}{\partial \alpha\_1} \right] - Q\_2 &= 0. \end{split} \tag{12}$$

The sixth equation is an identity expressing the equality of the moments of all forces acting on the element to zero relative to the axis normal to the surface of the element junction:

$$T\_1 - T\_2 - \frac{H\_1}{R\_1} + \frac{H\_2}{R\_2} = \mathbf{0}.$$

This equation was used to obtain Eq. (11).

#### **2.2 Border conditions**

The second and third integrals of expression in Eq. (8) give boundary conditions for the edges *α*<sup>1</sup> ¼ *const* and *α*<sup>2</sup> ¼ *const*, that is, for lines of principal curvatures.

*δ*Π ¼�

*Corrosion*

*a*ð2

*b* ð2

*∂N*1*A*<sup>2</sup> *∂α*<sup>1</sup>

� *N*<sup>1</sup>

*<sup>N</sup>*<sup>1</sup> � *<sup>N</sup><sup>α</sup>*<sup>1</sup> 1 � � *<sup>δ</sup><sup>u</sup>* <sup>þ</sup> *<sup>T</sup>*<sup>1</sup> � *<sup>H</sup>*<sup>1</sup>

> 1 *A*2 *∂H*<sup>1</sup> *∂α*<sup>2</sup>

2 � � *δ*

� �

� *N*<sup>2</sup>

*∂A*<sup>1</sup> *∂α*<sup>2</sup> þ *T*<sup>2</sup>

� *<sup>Q</sup><sup>α</sup>*<sup>1</sup> 1

> 1 *A*2 *∂w ∂α*<sup>2</sup> þ *v R*2

*<sup>Q</sup>*<sup>1</sup> <sup>¼</sup> <sup>1</sup> *A*1*A*<sup>2</sup>

*<sup>Q</sup>*<sup>2</sup> <sup>¼</sup> <sup>1</sup> *A*1*A*<sup>2</sup>

of the shell *α*<sup>1</sup> ¼ *const*, *α*<sup>2</sup> ¼ *const*.

Hamilton-Ostrogradsky principle.

*∂*N1A2 *∂*α<sup>1</sup>

*∂*T1A2 *∂*α<sup>1</sup>

*∂*Q1A2 *∂*α<sup>1</sup>

� N2

� N1

þ

� �

*∂*A2 *∂*α<sup>1</sup> þ

*∂*A1 *∂*α<sup>2</sup> þ

*∂*Q2A1 *∂*α<sup>2</sup>

� �

� �

**2.1 Equilibrium equations**

principle in Eq. (4).

equilibrium follow:

1 A1A2

1 A1A2

1 A1A2

**102**

*∂Q*2*A*<sup>1</sup> *∂α*<sup>2</sup>

*∂A*<sup>2</sup> *∂α*<sup>1</sup> þ

þ *A*1*A*<sup>2</sup>

*δw* �

� �

*∂A*<sup>2</sup> *∂α*<sup>1</sup>

� �

� �

*∂T*2*A*<sup>1</sup> *∂α*<sup>2</sup>

> � *<sup>A</sup>*1*A*<sup>2</sup> *R*2

*N*<sup>1</sup> *R*1 þ *N*<sup>2</sup> *R*2 � �

> *R*2 � *<sup>T</sup><sup>α</sup>*<sup>2</sup> 1

*A*2*dα*<sup>2</sup> þ

Here *Q*<sup>1</sup> and *Q*<sup>2</sup> are the transverse forces arising in the shell:

*∂M*1*A*<sup>2</sup> *∂α*<sup>1</sup>

*∂M*2*A*<sup>1</sup> *∂α*<sup>2</sup>

� �

þ *T*<sup>1</sup>

�� �

*∂A*<sup>1</sup> *∂α*<sup>2</sup>

*Q*<sup>2</sup> þ *A*1*A*2*p*<sup>2</sup>

þ *A*1*A*2*p*<sup>3</sup>

*<sup>T</sup>*<sup>2</sup> � *<sup>H</sup>*<sup>2</sup> *R*1 � *<sup>T</sup><sup>α</sup>*<sup>2</sup> 2

� �

*δv*

1 *A*1 *∂H*<sup>2</sup> *∂α*<sup>1</sup>

*∂A*<sup>2</sup> *∂α*<sup>1</sup>

*∂A*<sup>1</sup> *∂α*<sup>2</sup>

The last four terms in Eq. (8) is the work of concentrated forces along the edges

From Eq. (8), we obtain the equilibrium equation and boundary conditions.

In the mechanics of a solid deformable body, equilibrium equations can be obtained by making up for the main vector and the main moment of all the forces acting on the element for the infinitely small element extracted from the shell under the influence of external and internal forces (**Figure 2**). Here, the equilibrium equations and boundary conditions are obtained from the variational Lagrange

Note that in the case of dynamics, it is necessary to apply the variational

*∂*T2A1 *∂*α<sup>2</sup>

*∂*N2A1 *∂*α<sup>2</sup>

� N1 R1 þ N2 R2

So, from the first integral of expression in Eq. (8), the first three equations of

þ T1

þ T2

*∂*A1 *∂*α<sup>2</sup>

*∂*A2 *∂*α<sup>1</sup>

þ p3 ¼ 0*:*

� Q1 R1

� Q2 R2

þ p1 ¼ 0;

9 >>>>>>>=

>>>>>>>;

(11)

þ p2 ¼ 0;

þ *H*<sup>1</sup>

þ *H*<sup>2</sup>

� �

� �

*a*ð2

�

*a*1

þ *Q*<sup>2</sup> þ

�f g ½ � *H*<sup>1</sup> þ *H*<sup>2</sup> *δw <sup>b</sup>*2,*a*<sup>2</sup> þ f g ½ � *H*<sup>1</sup> þ *H*<sup>2</sup> *δw <sup>b</sup>*2,*a*<sup>2</sup> þ f g ½ � *H*<sup>1</sup> þ *H*<sup>2</sup> *δw <sup>b</sup>*1,*a*<sup>2</sup>

� *M*<sup>2</sup>

� *M*<sup>1</sup>

� *<sup>A</sup>*1*A*<sup>2</sup> *R*1

*Q*<sup>1</sup> þ *A*1*A*2*p*<sup>1</sup>

*dα*1*dα*2þ

*δu*

*δw* �

> *∂H*2*A*<sup>1</sup> *∂α*<sup>2</sup>

*∂H*1*A*<sup>2</sup> *∂α*<sup>1</sup>

1 *A*1 *∂w ∂α*<sup>1</sup> þ *u R*1

� �

<sup>þ</sup> *<sup>N</sup>*<sup>2</sup> � *<sup>N</sup><sup>α</sup>*<sup>2</sup>

2 � � *<sup>δ</sup>v*�

� f g ½ � *H*<sup>1</sup> þ *H*<sup>2</sup> *δw <sup>b</sup>*1,*a*<sup>1</sup>

; (9)

*:* (10)

*:*

�

(8)

þ

*δv*þ

1 � � *δ*

*δw* �

� *<sup>M</sup>*<sup>1</sup> � *<sup>M</sup><sup>α</sup>*<sup>1</sup>

� �

� *<sup>Q</sup><sup>α</sup>*<sup>2</sup> 2

> *∂A*<sup>2</sup> *∂α*<sup>2</sup> þ

*∂A*<sup>2</sup> *∂α*<sup>1</sup> þ *δu*þ

*b*1

*∂N*2*A*<sup>1</sup> *∂α*<sup>2</sup>

*∂Q*1*A*<sup>2</sup> *∂α*<sup>1</sup> þ

*a*1

þ

þ

þ *b* ð2

*b*1

þ *Q*<sup>1</sup> þ

� *<sup>M</sup>*<sup>2</sup> � *<sup>M</sup><sup>α</sup>*<sup>2</sup>

�

We emphasize that if one of the lines of the main curvatures is closed, then the displacements along this line will be periodic functions.

#### **2.3 Axisymmetric deformation of a cylindrical shell**

We introduce the following notation (**Figure 3**): R is the radius of the surface of the junction of a cylindrical bimetallic shell; l is the shell length; *δ*<sup>1</sup> and *δ*<sup>2</sup> are the thickness of the inner and outer layers; х is the distance from the left edge of the cylinder to the current section; *σ*<sup>1</sup> and *σ*<sup>2</sup> are normal stresses; *τ*<sup>13</sup> and is shear stress.

$$\begin{aligned} M\_1 &= \int\_0^{\delta\_1} \sigma\_1^{(1)} z dz + \int\_0^0 \sigma\_1^{(2)} z dz; N\_1 = \int\_0^{\delta\_1} \sigma\_1^{(1)} dz + \int\_{-\delta\_2}^0 \sigma\_1^{(2)} dz; \\ M\_2 &= \int\_0^{\delta\_1} \sigma\_2^{(1)} z dz + \int\_{-\delta\_2}^0 \sigma\_2^{(2)} z dz; N\_2 = \int\_0^{\delta\_1} \sigma\_2^{(1)} z dz + \int\_{-\delta\_2}^0 \sigma\_2^{(2)} z dz; \\ Q\_1 &= \int\_0^{\delta\_1} \sigma\_{13}^{(1)} \left( 1 - \frac{z}{R} \right) dz + \int\_1^0 \sigma\_{13}^{(2)} \left( 1 - \frac{z}{R} \right) dz. \end{aligned}$$

Relative deformations of a surface located at a distance z from the junction surface (**Figure 4**):

$$\varepsilon\_{1x} = \varepsilon\_1 - z\chi\_1; \ \chi\_1 = w''; \ \varepsilon\_{2x} = \varepsilon\_2 - z\chi\_2; \ \chi\_2 = \frac{w}{R^2}.$$

*σ*ð Þ<sup>2</sup> <sup>1</sup> <sup>¼</sup> *<sup>E</sup>*<sup>2</sup> 1 � *μ*<sup>2</sup> 2

**Figure 4.**

Power factors:

*<sup>B</sup>*<sup>1</sup> <sup>¼</sup> *<sup>E</sup>*1*δ*<sup>1</sup> 1 � *μ*<sup>2</sup> 1 þ

> *<sup>m</sup>*<sup>1</sup> <sup>¼</sup> <sup>1</sup> *δ*1

*δ* ð1

0

*E*2*δ*<sup>2</sup> 1 � *μ*<sup>2</sup> 2

*<sup>f</sup>* <sup>¼</sup> *<sup>E</sup>*1*δ*1*<sup>m</sup>* 1 � *μ*<sup>1</sup> þ

*<sup>β</sup>*1*tdz*; *<sup>m</sup>*<sup>2</sup> <sup>¼</sup> <sup>1</sup>

*Q*<sup>0</sup> <sup>1</sup> þ *M*<sup>2</sup>

*M*<sup>0</sup>

Equations of an infinitesimal element:

;*c*<sup>1</sup> <sup>¼</sup> <sup>1</sup> 2

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

*δ*2 ð 0

*N*<sup>1</sup> 1 þ *w*<sup>0</sup> ½ � ð Þ <sup>0</sup>

<sup>1</sup> � *Q*<sup>1</sup> ¼ 0*:*

�*δ*<sup>2</sup>

*<sup>R</sup>*<sup>2</sup> <sup>þ</sup> *<sup>N</sup>*1*w*<sup>0</sup> ½ �0

Here:

**105**

<sup>¼</sup> *<sup>E</sup>*<sup>2</sup> <sup>1</sup> � *<sup>μ</sup>*<sup>2</sup> 2

*Deformation of surface junction shell.*

*<sup>ε</sup>*<sup>1</sup> <sup>þ</sup> *<sup>μ</sup>*2*ε*<sup>2</sup> � *<sup>z</sup> <sup>χ</sup>*<sup>1</sup> <sup>þ</sup> *<sup>μ</sup>*2*χ*<sup>2</sup> ð Þ� <sup>1</sup> <sup>þ</sup> *<sup>μ</sup>*<sup>2</sup> ð Þ*β*2*<sup>T</sup>* � �; *<sup>σ</sup>*ð Þ<sup>2</sup>

*M*<sup>1</sup> ¼ *c*1*ε*<sup>1</sup> þ *c*2*ε*<sup>2</sup> � *D*1*χ*<sup>1</sup> � *D*2*χ*<sup>2</sup> � *g*; *N*<sup>1</sup> ¼ *B*1*ε*<sup>1</sup> þ *B*2*ε*<sup>2</sup> � *c*2*χ*<sup>2</sup> � *f*;

*M*<sup>2</sup> ¼ *c*2*ε*<sup>1</sup> þ *c*1*ε*<sup>2</sup> � *D*2*χ*<sup>1</sup> � *D*1*χ*<sup>2</sup> � *g*; *N*<sup>2</sup> ¼ *B*2*ε*<sup>1</sup> þ *B*1*ε*<sup>2</sup> � *c*2*χ*<sup>1</sup> � *c*1*χ*<sup>2</sup> � *f:*

; *<sup>g</sup>* <sup>¼</sup> <sup>1</sup> 2 *E*1*δ*<sup>2</sup> <sup>1</sup>*n*<sup>1</sup> 1 � *μ*<sup>1</sup>

*<sup>β</sup>*2*tdz*; *<sup>n</sup>*<sup>1</sup> <sup>¼</sup> <sup>2</sup>

þ *px* ¼ 0;

þ *N*<sup>2</sup>

*E*1*σ*<sup>2</sup> 1 1 � *μ*<sup>2</sup> 2 � 1 2

*E*2*δ*2*m* 1 � *μ*<sup>2</sup>

*<sup>ε</sup>*<sup>2</sup> <sup>þ</sup> *<sup>μ</sup>*2*ε*<sup>1</sup> � *<sup>z</sup> <sup>χ</sup>*<sup>2</sup> <sup>þ</sup> *<sup>μ</sup>*2*χ*<sup>1</sup> ð Þ� <sup>1</sup> <sup>þ</sup> *<sup>μ</sup>*<sup>2</sup> ð Þ*β*2*<sup>T</sup>* � �*:*ð Þ �*δ*<sup>2</sup> <sup>≤</sup>*z*≤<sup>0</sup>

*E*2*δ*<sup>2</sup> 2 1 � *μ*<sup>2</sup> 2

> *δ*2 1

*δ* ð1

0

*<sup>R</sup>* <sup>þ</sup> *pz* <sup>¼</sup> 0;

; *<sup>D</sup>*<sup>1</sup> <sup>¼</sup> <sup>1</sup> 3

> þ 1 2 *E*2*δ*<sup>2</sup> <sup>2</sup>*n*<sup>2</sup> 1 � *μ*<sup>2</sup> ;

*<sup>β</sup>*1*tzdz*; *<sup>n</sup>*<sup>2</sup> <sup>¼</sup> <sup>2</sup>

9 >>>>=

>>>>;

*E*1*δ*<sup>3</sup> 1 1 � *μ*<sup>2</sup> 1 þ 1 3

> *δ*2 2

ð 0

�*δ*<sup>2</sup>

*E*2*δ*<sup>3</sup> 2 1 � *μ*<sup>2</sup> 2 ;

*β*2*tzdz:*

2

Normal stresses according to Hooke's law:

$$\begin{split} \sigma\_{1}^{(1)} &= \frac{E\_{1}}{\mathbf{1} - \mu\_{1}^{2}} \left[ \varepsilon\_{1} + \mu\_{1}\varepsilon\_{2} - z(\chi\_{1} + \mu\_{1}\chi\_{2}) - (\mathbf{1} + \mu\_{1})\beta\_{1}\overline{T} \right]; \sigma\_{2}^{(1)} \\ &= \frac{E\_{1}}{\mathbf{1} - \mu\_{1}^{2}} \left[ \varepsilon\_{2} + \mu\_{1}\varepsilon\_{1} - z(\chi\_{2} + \mu\_{1}\chi\_{1}) - (\mathbf{1} + \mu\_{1})\beta\_{1}\overline{T} \right]; (\mathbf{0} \leq z \leq \delta\_{1}) \end{split}$$

**Figure 3.** *Element of cylindrical shell.*

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

**Figure 4.** *Deformation of surface junction shell.*

$$\sigma\_1^{(2)} = \frac{E\_2}{\mathbf{1} - \mu\_2^2} \left[ \varepsilon\_1 + \mu\_2 \varepsilon\_2 - z(\chi\_1 + \mu\_2 \chi\_2) - (\mathbf{1} + \mu\_2)\beta\_2 \overline{T} \right]; \sigma\_2^{(2)}$$

$$= \frac{E\_2}{\mathbf{1} - \mu\_2^2} \left[ \varepsilon\_2 + \mu\_2 \varepsilon\_1 - z(\chi\_2 + \mu\_2 \chi\_1) - (\mathbf{1} + \mu\_2)\beta\_2 \overline{T} \right]. (-\delta\_2 \le z \le 0)$$

Power factors:

$$M\_1 = c\_1 \mathbf{e}\_1 + c\_2 \mathbf{e}\_2 - D\_1 \boldsymbol{\chi}\_1 - D\_2 \boldsymbol{\chi}\_2 - \mathbf{g}; \\ N\_1 = B\_1 \mathbf{e}\_1 + B\_2 \mathbf{e}\_2 - c\_2 \boldsymbol{\chi}\_2 - f;$$

$$M\_2 = c\_2 \mathbf{e}\_1 + c\_1 \mathbf{e}\_2 - D\_2 \boldsymbol{\chi}\_1 - D\_1 \boldsymbol{\chi}\_2 - \mathbf{g}; \\ N\_2 = B\_2 \mathbf{e}\_1 + B\_1 \mathbf{e}\_2 - c\_2 \boldsymbol{\chi}\_1 - c\_1 \boldsymbol{\chi}\_2 - f.$$

Here:

We emphasize that if one of the lines of the main curvatures is closed, then the

We introduce the following notation (**Figure 3**): R is the radius of the surface of the junction of a cylindrical bimetallic shell; l is the shell length; *δ*<sup>1</sup> and *δ*<sup>2</sup> are the thickness of the inner and outer layers; х is the distance from the left edge of the cylinder to the current section; *σ*<sup>1</sup> and *σ*<sup>2</sup> are normal stresses; *τ*<sup>13</sup> and is shear stress.

<sup>1</sup> *zdz*; *N*<sup>1</sup> ¼

<sup>2</sup> *zdz*; *N*<sup>2</sup> ¼

*dz* þ

Relative deformations of a surface located at a distance z from the junction

*<sup>ε</sup>*1*<sup>z</sup>* <sup>¼</sup> *<sup>ε</sup>*<sup>1</sup> � *<sup>z</sup>χ*1; *<sup>χ</sup>*<sup>1</sup> <sup>¼</sup> *<sup>w</sup>*00; *<sup>ε</sup>*2*<sup>z</sup>* <sup>¼</sup> *<sup>ε</sup>*<sup>2</sup> � *<sup>z</sup>χ*2; *<sup>χ</sup>*<sup>2</sup> <sup>¼</sup> *<sup>w</sup>*

*<sup>ε</sup>*<sup>1</sup> <sup>þ</sup> *<sup>μ</sup>*1*ε*<sup>2</sup> � *<sup>z</sup> <sup>χ</sup>*<sup>1</sup> <sup>þ</sup> *<sup>μ</sup>*1*χ*<sup>2</sup> ð Þ� <sup>1</sup> <sup>þ</sup> *<sup>μ</sup>*<sup>1</sup> ð Þ*β*1*<sup>T</sup>* � �; *<sup>σ</sup>*ð Þ<sup>1</sup>

*<sup>ε</sup>*<sup>2</sup> <sup>þ</sup> *<sup>μ</sup>*1*ε*<sup>1</sup> � *<sup>z</sup> <sup>χ</sup>*<sup>2</sup> <sup>þ</sup> *<sup>μ</sup>*1*χ*<sup>1</sup> ð Þ� <sup>1</sup> <sup>þ</sup> *<sup>μ</sup>*<sup>1</sup> ð Þ*β*1*<sup>T</sup>* � �; 0ð Þ <sup>≤</sup> *<sup>z</sup>*≤*δ*<sup>1</sup>

*δ* ð1

0

*δ* ð1

0

ð 0

�*δ*<sup>2</sup> *τ* ð Þ2 <sup>13</sup> <sup>1</sup> � *<sup>z</sup> R* � �

*σ*ð Þ<sup>1</sup> <sup>1</sup> *dz* þ

*σ*ð Þ<sup>1</sup> <sup>2</sup> *zdz* þ ð 0

*σ*ð Þ<sup>2</sup> <sup>1</sup> *dz*;

*σ*ð Þ<sup>2</sup> <sup>2</sup> *zdz*;

*R*2 *:*

2

�*δ*<sup>2</sup>

ð 0

�*δ*<sup>2</sup>

*dz:*

displacements along this line will be periodic functions.

**2.3 Axisymmetric deformation of a cylindrical shell**

*M*<sup>1</sup> ¼

*M*<sup>2</sup> ¼

surface (**Figure 4**):

*Corrosion*

*σ*ð Þ<sup>1</sup> <sup>1</sup> <sup>¼</sup> *<sup>E</sup>*<sup>1</sup> <sup>1</sup> � *<sup>μ</sup>*<sup>2</sup> 1

**Figure 3.**

**104**

*Element of cylindrical shell.*

<sup>¼</sup> *<sup>E</sup>*<sup>1</sup> 1 � *μ*<sup>2</sup> 1

*δ* ð1

0

*σ*ð Þ<sup>1</sup> <sup>2</sup> *zdz* þ

*Q*<sup>1</sup> ¼

Normal stresses according to Hooke's law:

*δ* ð1

0 *τ* ð Þ1 <sup>13</sup> <sup>1</sup> � *<sup>z</sup> R* � �

*δ* ð1

0

*σ*ð Þ<sup>1</sup> <sup>1</sup> *zdz* þ ð 0

*σ*ð Þ<sup>2</sup>

*σ*ð Þ<sup>2</sup>

�*δ*<sup>2</sup>

ð 0

�*δ*<sup>2</sup>

$$B\_{1} = \frac{E\_{1}\delta\_{1}}{1-\mu\_{1}^{2}} + \frac{E\_{2}\delta\_{2}}{1-\mu\_{2}^{2}}; c\_{1} = \frac{1}{2}\frac{E\_{1}\sigma\_{1}^{2}}{1-\mu\_{2}^{2}} - \frac{1}{2}\frac{E\_{2}\delta\_{2}^{2}}{1-\mu\_{2}^{2}}; D\_{1} = \frac{1}{3}\frac{E\_{1}\delta\_{1}^{3}}{1-\mu\_{1}^{2}} + \frac{1}{3}\frac{E\_{2}\delta\_{2}^{3}}{1-\mu\_{2}^{2}};$$

$$f = \frac{E\_{1}\delta\_{1}m}{1-\mu\_{1}} + \frac{E\_{2}\delta\_{2}m}{1-\mu\_{2}}; g = \frac{1}{2}\frac{E\_{1}\delta\_{1}^{2}n\_{1}}{1-\mu\_{1}} + \frac{1}{2}\frac{E\_{2}\delta\_{2}^{2}n\_{2}}{1-\mu\_{2}};$$

$$m\_{1} = \frac{1}{\delta\_{1}}\int\_{0}^{\delta\_{1}}\beta\_{1}t dz; m\_{2} = \frac{1}{\delta\_{2}}\int\_{0}^{0}\beta\_{2}t dz; n\_{1} = \frac{2}{\delta\_{1}^{2}}\int\_{0}^{\delta\_{1}}\beta\_{1}t z dz; n\_{2} = \frac{2}{\delta\_{2}^{2}}\int\_{-\delta\_{2}}^{0}\beta\_{2}t z dz.$$

Equations of an infinitesimal element:

$$\begin{aligned} \left[N\_1(\mathbf{1} + \boldsymbol{\nu}')\right]' + p\_x &= \mathbf{0};\\ \left[Q\_1' + \frac{M\_2}{R^2} + \left[N\_1\boldsymbol{\nu}'\right]' + \frac{N\_2}{R} + p\_x &= \mathbf{0};\\ \left[M\_1' - \mathbf{Q}\_1 = \mathbf{0}.\end{aligned}\right] $$

#### *Corrosion*

The problem of axisymmetric deformation of an elastic bimetallic cylindrical shell for any relations between thicknesses, different mechanical characteristics of the material of the layers, and arbitrary heating along the thickness and axial direction is described by the equation:

*w* ¼ *k*1*chαx* cos *βx* þ *k*2*shαx* sin *βx* þ *k*3*shαx* cos *βx* þ *k*4*chαx* sin *βx*, (15)

ffiffiffiffiffiffi *b*�*a* 2 q

For an infinitely long shell in solution in Eq. (15),*shαx* and*ch*ð Þ *αx* we express it in

*w* ¼ *k*1*A*1ð Þþ *αx*, *βx T*2*A*2ð Þþ *αx*, *βx w*0*:*

terms of exponential functions. As x ! ∞, terms containing exp. αx ! ∞ and

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

; *β* ¼

�*α<sup>x</sup>* sin *<sup>β</sup>x*; *<sup>A</sup>*<sup>2</sup> <sup>¼</sup> *<sup>A</sup>*2ð Þ¼ *<sup>α</sup>x*, *<sup>β</sup><sup>x</sup> <sup>e</sup>*

1 *<sup>E</sup>*<sup>1</sup> � <sup>1</sup> *E*2 � � *<sup>R</sup>*<sup>2</sup>

> *kA h*

*<sup>c</sup>* � *<sup>R</sup>*<sup>2</sup> *b* � ��<sup>1</sup>

> 1 *<sup>E</sup>*<sup>1</sup> � <sup>1</sup> *E*2 � � *<sup>R</sup>*<sup>2</sup>

1 *E*<sup>1</sup> *R*<sup>2</sup> *<sup>c</sup>*�*R*<sup>2</sup> ð Þ*<sup>b</sup>*

The initial thickness *h*<sup>0</sup> is taken constant for all points of the two-layer shell.

*Geometry and loads acting on an element of two-layer shell: 1—outer layer; 2—inner layer; qa—internal*

*b*�*R*<sup>2</sup> *a Rc*�*R*<sup>2</sup> *a*

*<sup>b</sup>* � *<sup>R</sup>*<sup>2</sup> *a* � ��<sup>1</sup> ; (16)

� �; (17)

� <sup>1</sup> *R*2 *<sup>c</sup>* � *<sup>R</sup>*<sup>2</sup> *b*

9 = ;

<sup>þ</sup> *<sup>E</sup>*�<sup>1</sup> <sup>2</sup> *R*<sup>2</sup>

*b*�*R*<sup>2</sup> *a R*2 *c*�*R*<sup>2</sup> *a* � �

*h*ð Þ¼ 0 *h*0, *h*<sup>0</sup> ¼ *Rc* � *Ra:* (18)

<sup>þ</sup> <sup>1</sup> *E*<sup>2</sup> *R*<sup>2</sup> *<sup>b</sup>*�*R*<sup>2</sup> ð Þ*<sup>a</sup>*

Example 1. Consider a bimetallic cylindrical shell under the influence of internal

In this case, the stress intensity is constant for all points of the shell and is equal

ffiffiffiffiffiffi *b*þ*a* 2 q .

�*α<sup>x</sup>* cos *βx:*

k1, … *k*<sup>4</sup> are arbitrary constants; *α* ¼

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

*A*<sup>1</sup> ¼ *A*1ð Þ¼ *αx*, *βx e*

pressure q and a corrosive medium (**Figure 5**).

� *<sup>Q</sup> R*2 *<sup>c</sup>* � *<sup>R</sup>*<sup>2</sup> *b*

Given Eq. (16), Eq. (3) takes the form:

*A* ¼ *q R*ð Þ *<sup>c</sup>* � *Ra*

with the initial condition:

; *Q* ¼ *q*

*dh*

8 < :

*R*2 *a R*2 *<sup>c</sup>* � *<sup>R</sup>*<sup>2</sup> *a* �

*E*�<sup>1</sup> <sup>1</sup> *R*<sup>2</sup>

*dt* ¼ �*αφ*ð Þ*<sup>t</sup>* <sup>1</sup> <sup>þ</sup>

integration constants ! 0.

Then:

Here

to [5]:

**Figure 5.**

*pressure.*

**107**

*<sup>σ</sup><sup>i</sup>* <sup>¼</sup> *qR*<sup>2</sup>

*a R*2 *<sup>c</sup>* � *<sup>R</sup>*<sup>2</sup> *a*

$$\mathbf{w}^{\rm IV} + 2\mathbf{a}\mathbf{w}'' + \mathbf{b}^2 \mathbf{w} = \boldsymbol{\theta}(\mathbf{x}).\tag{13}$$

$$a = \frac{1}{R} \frac{c\_2 B\_1 - c\_1 B\_2 - \mathbf{1}\_2 B\_1 R N\_1}{D\_1 B\_1 - c\_1^2}; b^2 = \frac{1}{R^2} \frac{B\_1^2 - B\_2^2}{D\_1 B\_1 - c\_1^2};$$

$$\boldsymbol{\theta}(\mathbf{x}) = \frac{B\_1}{D\_1 B\_1 - c\_1^2} \left\{ \frac{c\_1}{B\_1} (N\_1 + f)'' + \frac{\mathbf{1}\_2 B\_2}{R B\_1} \left[ N\_1 + \left( \mathbf{1} - \frac{B\_1}{B\_2} \right) f \right] - \mathbf{g}'' - p\_x \right\}.$$

Consider the case:

$$c\_1 = c\_2 = 0; \mu\_1 = \mu\_2 = \mu; E\_1 \delta\_1^2 = E\_2 \delta\_2^2.$$

Then the force factors are written as follows:

$$M\_1 = -D[w'' + (1 + \mu)n]; N\_1 = B\left[\varepsilon\_1 - \mu \frac{w}{R} - (1 + \mu)m\right];$$

$$M\_2 = -D[\mu w'' + (1 + \mu)n]; N\_2 = \mu N\_1 - \frac{B}{R}(1 - \mu^2)(w + mR).$$

Here

$$B = \frac{\delta\sqrt{E\_1 E\_2}}{1 - \mu^2}; D = \frac{1}{3} \frac{E\_1 E\_2 \delta^3}{(1 - \mu^2)\left(\sqrt{E\_1} + \sqrt{E\_2}\right)^2};$$

$$m = \frac{m\_1 + m\_2\sqrt{E\_2/E\_1}}{1 + \sqrt{E\_2/E\_1}}; n = \frac{3}{2} \frac{n\_1 + n\_2}{\delta};$$

$$k^4 = \sqrt[4]{\frac{(1 - \mu^2)B}{4DR^2}} = \frac{\sqrt[4]{3(1 - \mu^2)}}{\sqrt{2R\delta}} \frac{\sqrt{\sqrt{E\_1} + \sqrt{E\_2}}}{\sqrt[4]{E\_1 E\_2}}.$$

In this case, instead of Eq. (13), we obtain the following equation:

$$w^{IV} - \frac{RN\_1}{D}w'' + 4k^4w = \frac{4k^4B}{(1-\mu^2)B} \left(\mu N\_1 + p\_x R\right) - 4k^4Rm - (1+\mu)n''.\tag{14}$$

The boundary conditions for bimetallic shells coincide with similar conditions for homogeneous shells.

So, for a hard-pressed edge we get:

$$w = \frac{\partial w}{\partial \mathbf{n}} = \mathbf{0}$$

For the free edge we have:

$$M\_1 = Q\_1 = 0$$

#### **2.4 Infinitely long cylindrical shell (piping)**

We write the solution of the homogeneous Eq. (13) in the following form:

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

*w* ¼ *k*1*chαx* cos *βx* þ *k*2*shαx* sin *βx* þ *k*3*shαx* cos *βx* þ *k*4*chαx* sin *βx*, (15)

k1, … *k*<sup>4</sup> are arbitrary constants; *α* ¼ ffiffiffiffiffiffi *b*�*a* 2 q ; *β* ¼ ffiffiffiffiffiffi *b*þ*a* 2 q .

For an infinitely long shell in solution in Eq. (15),*shαx* and*ch*ð Þ *αx* we express it in terms of exponential functions. As x ! ∞, terms containing exp. αx ! ∞ and integration constants ! 0.

Then:

The problem of axisymmetric deformation of an elastic bimetallic cylindrical shell for any relations between thicknesses, different mechanical characteristics of the material of the layers, and arbitrary heating along the thickness and axial

w ¼ θð Þ x *:* (13)

*f*

� *g*<sup>00</sup> � *pz*

;

*Rm* � ð Þ 1 þ *μ n*00*:* (14)

*:*

*B*2 <sup>1</sup> � *<sup>B</sup>*<sup>2</sup> 2 *<sup>D</sup>*1*B*<sup>1</sup> � *<sup>c</sup>*<sup>2</sup> 1 ;

*B*2 � �

wIV <sup>þ</sup> 2aw<sup>00</sup> <sup>þ</sup> b2

*<sup>D</sup>*1*B*<sup>1</sup> � *<sup>c</sup>*<sup>2</sup> 1

ð Þ *N*<sup>1</sup> þ *f* <sup>00</sup> þ

*M*<sup>1</sup> ¼ �*D w*<sup>00</sup> ½ � þ ð Þ 1 þ *μ n* ; *N*<sup>1</sup> ¼ *B ε*<sup>1</sup> � *μ*

*<sup>M</sup>*<sup>2</sup> ¼ �*<sup>D</sup> <sup>μ</sup>w*<sup>00</sup> ½ � <sup>þ</sup> ð Þ <sup>1</sup> <sup>þ</sup> *<sup>μ</sup> <sup>n</sup>* ; *<sup>N</sup>*<sup>2</sup> <sup>¼</sup> *<sup>μ</sup>N*<sup>1</sup> � *<sup>B</sup>*

<sup>1</sup> � *<sup>μ</sup>*<sup>2</sup> ; *<sup>D</sup>* <sup>¼</sup> <sup>1</sup>

*<sup>m</sup>* <sup>¼</sup> *<sup>m</sup>*<sup>1</sup> <sup>þ</sup> *<sup>m</sup>*<sup>2</sup>

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi 1 � *μ*<sup>2</sup> ð Þ*B* 4*DR*<sup>2</sup>

*<sup>w</sup>* <sup>¼</sup> <sup>4</sup>*k*<sup>4</sup>

3

¼

In this case, instead of Eq. (13), we obtain the following equation:

*B*

ffiffiffiffiffiffiffiffiffiffiffiffi *E*2*=E*<sup>1</sup> p <sup>1</sup> <sup>þ</sup> ffiffiffiffiffiffiffiffiffiffiffiffi *E*2*=E*<sup>1</sup> <sup>p</sup> ; *<sup>n</sup>* <sup>¼</sup> <sup>3</sup>

*=*<sup>2</sup>*B*1*RN*<sup>1</sup>

*<sup>c</sup>*<sup>1</sup> <sup>¼</sup> *<sup>c</sup>*<sup>2</sup> <sup>¼</sup> 0; *<sup>μ</sup>*<sup>1</sup> <sup>¼</sup> *<sup>μ</sup>*<sup>2</sup> <sup>¼</sup> *<sup>μ</sup>*; *<sup>E</sup>*1*δ*<sup>2</sup>

1 *R B*2 *B*1 ; *<sup>b</sup>*<sup>2</sup> <sup>¼</sup> <sup>1</sup> *R*2

� �

*<sup>N</sup>*<sup>1</sup> <sup>þ</sup> <sup>1</sup> � *<sup>B</sup>*<sup>1</sup>

� �

<sup>1</sup> <sup>¼</sup> *<sup>E</sup>*2*δ*<sup>2</sup> 2*:*

*w*

*R*

*E*1*E*2*δ*<sup>3</sup>

2

*E*1 <sup>p</sup> <sup>þ</sup> ffiffiffiffiffi *E*2 � � <sup>p</sup> <sup>2</sup> ;

> *n*<sup>1</sup> þ *n*<sup>2</sup> *<sup>δ</sup>* ;

p p ffiffiffiffiffiffiffiffiffiffi *E*1*E*<sup>2</sup> p<sup>3</sup> *:*

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi ffiffiffiffiffi *E*1 <sup>p</sup> <sup>þ</sup> ffiffiffiffiffi *E*2

<sup>1</sup> � *<sup>μ</sup>*<sup>2</sup> ð Þ ffiffiffiffiffi

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi 3 1 � *<sup>μ</sup>*<sup>2</sup> ð Þ <sup>p</sup><sup>4</sup> ffiffiffiffiffiffiffiffi <sup>2</sup>*R<sup>δ</sup>* <sup>p</sup>

<sup>1</sup> � *<sup>μ</sup>*<sup>2</sup> ð Þ*<sup>B</sup> <sup>μ</sup>N*<sup>1</sup> <sup>þ</sup> *pzR* � � � <sup>4</sup>*k*<sup>4</sup>

The boundary conditions for bimetallic shells coincide with similar conditions

*<sup>∂</sup><sup>n</sup>* <sup>¼</sup> <sup>0</sup>

*M*<sup>1</sup> ¼ *Q*<sup>1</sup> ¼ 0

We write the solution of the homogeneous Eq. (13) in the following form:

*<sup>w</sup>* <sup>¼</sup> *<sup>∂</sup><sup>w</sup>*

*<sup>R</sup>* � ð Þ <sup>1</sup> <sup>þ</sup> *<sup>μ</sup> <sup>m</sup>* h i

<sup>1</sup> � *<sup>μ</sup>*<sup>2</sup> � �ð Þ *<sup>w</sup>* <sup>þ</sup> *mR :*

*c*2*B*<sup>1</sup> � *c*1*B*<sup>2</sup> � <sup>1</sup>

*c*1 *B*1

Then the force factors are written as follows:

*<sup>B</sup>* <sup>¼</sup> *<sup>δ</sup>* ffiffiffiffiffiffiffiffiffiffi *E*1*E*<sup>2</sup> p

*<sup>k</sup>*<sup>4</sup> <sup>¼</sup>

*<sup>D</sup> <sup>w</sup>*<sup>00</sup> <sup>þ</sup> <sup>4</sup>*k*<sup>4</sup>

For the free edge we have:

So, for a hard-pressed edge we get:

**2.4 Infinitely long cylindrical shell (piping)**

4 r

direction is described by the equation:

*<sup>a</sup>* <sup>¼</sup> <sup>1</sup> *R*

*B*1 *<sup>D</sup>*1*B*<sup>1</sup> � *<sup>c</sup>*<sup>2</sup> 1

*θ*ð Þ¼ *x*

*Corrosion*

Here

*<sup>w</sup>IV* � *RN*<sup>1</sup>

**106**

for homogeneous shells.

Consider the case:

$$w = k\_1 A\_1(a\infty, \beta \infty) + T\_2 A\_2(a\infty, \beta \infty) + w\_0.1$$

Here

$$A\_1 = A\_1(a\infty, \beta\infty) = e^{-a\infty}\sin\beta\infty; A\_2 = A\_2(a\infty, \beta\infty) = e^{-a\infty}\cos\beta\infty.$$

Example 1. Consider a bimetallic cylindrical shell under the influence of internal pressure q and a corrosive medium (**Figure 5**).

In this case, the stress intensity is constant for all points of the shell and is equal to [5]:

$$\sigma\_{i} = \frac{qR\_{a}^{2}}{R\_{c}^{2} - R\_{a}^{2}} - \frac{Q}{R\_{c}^{2} - R\_{b}^{2}}; Q = q \frac{\left(\frac{1}{E\_{1}} - \frac{1}{E\_{2}}\right) \frac{R\_{b}^{2} - R\_{a}^{2}}{R\_{c} - R\_{a}^{2}}}{E\_{1}^{-1} \left(R\_{c}^{2} - R\_{b}^{2}\right)^{-1} + E\_{2}^{-1} \left(R\_{b}^{2} - R\_{a}^{2}\right)^{-1}};\tag{16}$$

Given Eq. (16), Eq. (3) takes the form:

$$\frac{dh}{dt} = -a\rho(t)\left(1 + \frac{kA}{h}\right);\tag{17}$$

$$A = q(R\_c - R\_a)\left\{\frac{R\_a^2}{R\_c^2 - R\_a^2} - \frac{\left(\frac{1}{E\_1} - \frac{1}{E\_2}\right)\left(\frac{R\_b^2 - R\_a^2}{R\_c^2 - R\_a^2}\right)}{\frac{1}{E\_1\left(R\_c^2 - R\_b^2\right)} + \frac{1}{E\_2\left(R\_b^2 - R\_a^2\right)}} \cdot \frac{1}{R\_c^2 - R\_b^2}\right\}$$

with the initial condition:

$$h(\mathbf{0}) = h\_0,\\ h\_0 = R\_c - R\_a. \tag{18}$$

The initial thickness *h*<sup>0</sup> is taken constant for all points of the two-layer shell.

**Figure 5.**

*Geometry and loads acting on an element of two-layer shell: 1—outer layer; 2—inner layer; qa—internal pressure.*

Eq. (17) with the initial condition Eq. (18) is integrated in quadratures:

$$h = h\_0 - kP \ln \frac{h\_0 k A}{h + kA} - \alpha \int\_0^\tau \rho(t) dt, h > 0. \tag{19}$$

In case *φ* � 1, expression in Eq. (19) takes the form:

$$h = h\_0 - at - kP \ln \frac{h\_0 + kA}{h + kA}, h > 0. \tag{20}$$

We note that Eq. (20) differs from linear equation *h* ¼ *h*<sup>0</sup> � *αt* by the presence of an additional term that takes into account the effect of the stress state of the twolayer shell on the corrosion rate.

Let us determine the durability of a steel two-layer cylindrical shell with *Rc* = 80.0 cm; *h*<sup>0</sup> ¼ *Rc* � *Ra* ¼ 0*:*8 cm; *h*<sup>1</sup> ¼ *Rc* � *Rb* ¼ 0*:*5 cm; *h*<sup>2</sup> ¼ *Rb* � *Ra* ¼ 0, 3cm; q = 10 kg/cm2 ; and [σT] = 2200 kg/cm2 ; *<sup>E</sup>*<sup>1</sup> <sup>¼</sup> *<sup>E</sup>*<sup>2</sup> <sup>¼</sup> <sup>2</sup> � 106 kg/cm2 .

Corrosion rate, *dh dt* � � � � *<sup>σ</sup><sup>i</sup>* <sup>¼</sup> *<sup>α</sup>* <sup>¼</sup> <sup>0</sup>*:*03 cm/year [2]; *dh dt* � � � � *<sup>σ</sup>i*¼½ � *<sup>σ</sup><sup>T</sup>* <sup>¼</sup> *<sup>α</sup>*<sup>1</sup> <sup>¼</sup> <sup>0</sup>*:*05cm/year [2], where [σТ] is the allowable value of stress intensity at the end of the service life.

Given Eq. (3) we get:

$$k = \frac{a\_1/a - 1}{[\sigma\_T]}.$$

The final value of the thickness of the shell *hT* is found from the conditions of achievement *σij* ¼ ½ � *σ<sup>T</sup>* :

$$h\_T = \frac{A}{\left[\sigma\_T\right]} = \mathbf{0.315 cm.}$$

Substituting the values of the coefficients in Eq. (3), we find the durability T = 11.6 years. In conventional calculations, the durability is calculated by the formula: *<sup>T</sup>* <sup>¼</sup> *<sup>h</sup>*0�*hT <sup>α</sup>*<sup>1</sup> , where T = 9.7 years.

In conclusion, it should be noted that in the general case it is necessary to solve the unrelated problem of the theory of shells [10, 11], when at each step of integration over time it is necessary to solve the problem of the stress-strain state of a bimetallic shell by a variable thickness, for which it is necessary to use methods of integrating partial equations derivatives [12, 13].

#### **3. The durability of the rotor blades of centrifugal pumps when exposed to corrosion wear**

The impellers of centrifugal pumps subjected to corrosion are usually thinwalled plates and shells. The problem of the durability of the elements of the impellers of centrifugal pumps is the problem of the durability of the plates and shells of a variable thickness over time, under the influence of an aggressive environment with certain parameters (degree of chemical activity, temperature, flow rate, etc.), and the stress-strain state.

The rate of change of thickness at a given point of the blade is taken in the form

*dt* <sup>¼</sup> *F t*ð Þ , *<sup>T</sup>*, *<sup>σ</sup>* (21)

*h x*ð Þ¼ , *y*, 0 *h*0ð Þ *x*, *y* , (22)

*dh*

of a functional relationship:

*Geometry and coordinate system of centrifugal pump blade.*

**Figure 7.**

**109**

**Figure 6.**

*Scheme of centrifugal pump: 1—confuser; 2—impeller; 3—diffuser.*

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

with the initial condition:

**Figure 6** shows the layout of a centrifugal pump. Consider the durability of the working blades of centrifugal pumps, which are a trapezoidal shell of variable stiffness (**Figure 7**). The blade is subject to the combined action of centrifugal load and corrosion wear.

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

**Figure 6.** *Scheme of centrifugal pump: 1—confuser; 2—impeller; 3—diffuser.*

#### **Figure 7.**

Eq. (17) with the initial condition Eq. (18) is integrated in quadratures:

*<sup>h</sup>* <sup>¼</sup> *<sup>h</sup>*<sup>0</sup> � *<sup>α</sup><sup>t</sup>* � *kP* ln *<sup>h</sup>*<sup>0</sup> <sup>þ</sup> *kA*

Let us determine the durability of a steel two-layer cylindrical shell with

*<sup>σ</sup><sup>i</sup>* <sup>¼</sup> *<sup>α</sup>* <sup>¼</sup> <sup>0</sup>*:*03 cm/year [2]; *dh*

*hT* <sup>¼</sup> *<sup>A</sup>* ½ � *σ<sup>T</sup>*

*<sup>α</sup>*<sup>1</sup> , where T = 9.7 years.

integrating partial equations derivatives [12, 13].

where [σТ] is the allowable value of stress intensity at the end of the service life.

*<sup>k</sup>* <sup>¼</sup> *<sup>α</sup>*1*=<sup>α</sup>* � <sup>1</sup> ½ � *σ<sup>Т</sup>*

The final value of the thickness of the shell *hT* is found from the conditions of

Substituting the values of the coefficients in Eq. (3), we find the durability T = 11.6 years. In conventional calculations, the durability is calculated by the

In conclusion, it should be noted that in the general case it is necessary to solve the unrelated problem of the theory of shells [10, 11], when at each step of integration over time it is necessary to solve the problem of the stress-strain state of a bimetallic shell by a variable thickness, for which it is necessary to use methods of

**3. The durability of the rotor blades of centrifugal pumps when exposed**

The impellers of centrifugal pumps subjected to corrosion are usually thinwalled plates and shells. The problem of the durability of the elements of the impellers of centrifugal pumps is the problem of the durability of the plates and shells of a variable thickness over time, under the influence of an aggressive environment with certain parameters (degree of chemical activity, temperature, flow

**Figure 6** shows the layout of a centrifugal pump. Consider the durability of the

working blades of centrifugal pumps, which are a trapezoidal shell of variable stiffness (**Figure 7**). The blade is subject to the combined action of centrifugal load

*<sup>h</sup>* <sup>þ</sup> *kA* � *<sup>α</sup>*

We note that Eq. (20) differs from linear equation *h* ¼ *h*<sup>0</sup> � *αt* by the presence of an additional term that takes into account the effect of the stress state of the two-

*Rc* = 80.0 cm; *h*<sup>0</sup> ¼ *Rc* � *Ra* ¼ 0*:*8 cm; *h*<sup>1</sup> ¼ *Rc* � *Rb* ¼ 0*:*5 cm; *h*<sup>2</sup> ¼ *Rb* � *Ra* ¼ 0, 3cm;

ð*τ*

*φ*ð Þ*t dt*, *h*>0*:* (19)

*<sup>h</sup>* <sup>þ</sup> *kA* , *<sup>h</sup>*>0*:* (20)

.

*<sup>σ</sup>i*¼½ � *<sup>σ</sup><sup>T</sup>* <sup>¼</sup> *<sup>α</sup>*<sup>1</sup> <sup>¼</sup> <sup>0</sup>*:*05cm/year [2],

0

; *<sup>E</sup>*<sup>1</sup> <sup>¼</sup> *<sup>E</sup>*<sup>2</sup> <sup>¼</sup> <sup>2</sup> � 106 kg/cm2

*dt* � � � �

*:*

¼ 0*:*315 cm*:*

*<sup>h</sup>* <sup>¼</sup> *<sup>h</sup>*<sup>0</sup> � *kP* ln *<sup>h</sup>*0*kA*

In case *φ* � 1, expression in Eq. (19) takes the form:

; and [σT] = 2200 kg/cm2

*dt* � � � �

layer shell on the corrosion rate.

q = 10 kg/cm2

*Corrosion*

Corrosion rate, *dh*

achievement *σij* ¼ ½ � *σ<sup>T</sup>* :

formula: *<sup>T</sup>* <sup>¼</sup> *<sup>h</sup>*0�*hT*

**to corrosion wear**

and corrosion wear.

**108**

rate, etc.), and the stress-strain state.

Given Eq. (3) we get:

*Geometry and coordinate system of centrifugal pump blade.*

The rate of change of thickness at a given point of the blade is taken in the form of a functional relationship:

$$\frac{dh}{dt} = F(t, T, \sigma) \tag{21}$$

with the initial condition:

$$h(\mathfrak{x}, \mathfrak{y}, \mathbf{0}) = h\_0(\mathfrak{x}, \mathfrak{y}), \tag{22}$$

where x, y are the coordinates of the middle surface of the scapula; T is the temperature; and σ is the function connecting the rate of change of thickness with the stress state at a surface point. Function F should be determined from experiment.

Assuming that the rate of change in corrosion wear is a linear function of stress intensity, we write Eq. (21) in the form:

$$\frac{dh}{dt} = \rho(t) \left(\mathbf{1} + k\sigma\_{\circ}\right). \tag{23}$$

*w* ¼ *w*,*<sup>n</sup>* ¼ *F* ¼ *F*,*<sup>n</sup>* ¼ 0*:* (28)

*<sup>∂</sup><sup>η</sup>* <sup>¼</sup> <sup>0</sup>*:* (29)

ð Þ i ¼ 0, 1, … , n; j ¼ 0, 1, … , m *:* (30)

þ *L* ¼ 0, (32)

*<sup>∂</sup>η*<sup>3</sup> ; *<sup>L</sup>* <sup>¼</sup> *BX* <sup>þ</sup> *<sup>b</sup>:*

(31)

The boundary conditions at the inlet and outlet edges of the blade correspond to

The important issue is to specify the function of changing the blade thickness h =

In our studies, the function of changing the blade thickness was set in the form

In the general case, the blade thickness can be represented as two-dimensional

� �*<sup>β</sup>*

*ξi*, *ξ*<sup>i</sup>þ1; *η*<sup>j</sup>

h i

is a bicubic polynomial, continuous, and has continuous partial derivatives up to

, *η*<sup>j</sup>þ<sup>1</sup>

� � <sup>¼</sup> *<sup>L</sup>*1;

)

� � <sup>¼</sup> *<sup>L</sup>*2,

*∂*3 *X*

*<sup>N</sup><sup>ξ</sup>* <sup>¼</sup> *<sup>N</sup>ξη* <sup>¼</sup> *<sup>M</sup><sup>ξ</sup>* <sup>¼</sup> 0; *<sup>Q</sup><sup>ξ</sup>* � *<sup>∂</sup>Mξη*

the free edge. In this case we have:

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

of cubic splines [9].

spline interpolations:

and including *<sup>∂</sup>*4*h*ð Þ *<sup>ξ</sup>*, *<sup>η</sup>*

divergent form:

X 3

X 3

*A*ð Þ*ij*

*αβ <sup>ξ</sup>* � *<sup>ξ</sup><sup>i</sup>* ð Þ*<sup>α</sup> <sup>η</sup>* � *<sup>η</sup> <sup>j</sup>*

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

This function on each element of the surface of the scapula

We represent the system of Eq. (24) in a dimensionless form:

*L*11ð Þþ *w L*<sup>12</sup> *F*

L21ð Þþ *w L*<sup>22</sup> *F*

where *Lik*ð Þ *i*, *k* ¼ 1, 2 are dimensionless differential operators of the theory of shells, referred to the lines of curvature of the surface; *Lm* ð Þ m ¼ 1, 2 are

is based on the application of the method of integral relations by Dorodnitsyn [13]. In accordance with the method, we write the initial system of Eq. (31) in

> *∂Y ∂η*

*z*<sup>1</sup> ¼ *w*,1; *z*<sup>2</sup> ¼ *w*,11; *z*<sup>3</sup> ¼ *w*,111; *z*<sup>4</sup> ¼ *F*,1; *z*<sup>5</sup> ¼ *F*,11; *z*<sup>6</sup> ¼ *F*,111*:*

In Eq. (32) *Br* ¼ f g *bmn*,*<sup>s</sup>* and *B* ¼ f g *bmn* ;(s = 0, 1, 2, 3; m, n = 1, 2, ..., 8) are

*∂X ∂ξ* þ

� �;

*∂X ∂η* þ *B*<sup>2</sup> *∂*2 *X <sup>∂</sup>η*<sup>2</sup> <sup>þ</sup> *<sup>B</sup>*<sup>3</sup>

The analytical solution of the system of Eq. (31) with boundary conditions in Eq. (28)

*<sup>∂</sup>ξ*2*∂η*<sup>2</sup> , that is *<sup>h</sup>*ð Þ *<sup>ξ</sup>*, *<sup>η</sup>* <sup>∈</sup>*c*2,2.

components of a given surface and temperature load.

where *X* ¼ f g *Xi* ¼ *w*, z1, *z*2, *z*3, *F*, *z*4, *z*5, *z*<sup>6</sup>

*Y* ¼ *B*0*X* þ *B*<sup>1</sup>

Through *z*1, … , z6 marked:

transformation matrices.

**111**

*β*¼0

*α*¼0

*h ξi*, *η<sup>i</sup>* ð Þ¼ *h*<sup>0</sup>

h (x, y) in the process of erosion-corrosion wear.

Eq. (23) must be supplemented with shell theory equations of variable thickness.

Omitting the intermediate calculations, we present a system of partial differential equations of the type Margherra [14] with respect to the normal deflection w and the stress function F of the eighth order, describing the stress state of the blade of variable thickness, taking into account the temperature effect:

$$\begin{split} D\nabla^4 w &+ 2\frac{\partial D}{\partial \mathbf{x}} \frac{\partial}{\partial \mathbf{x}} \nabla^2 w + 2\frac{\partial D}{\partial \mathbf{y}} \frac{\partial}{\partial \mathbf{y}} \nabla^2 w + \nabla^2 D \nabla^2 w - (1 - \nu) L(D, W) - h \nabla^2\_k F \\ &= q - \nabla^2 M\_T; \frac{1}{B} \nabla^4 F + 2\frac{\partial}{\partial \mathbf{x}} \left( \frac{1}{B} \right) \frac{\partial}{\partial \mathbf{x}} \nabla^2 F + 2\frac{\partial}{\partial \mathbf{y}} \left( \frac{1}{B} \right) \frac{\partial}{\partial \mathbf{y}} \nabla^2 F + \nabla^2 \left( \frac{1}{B} \right) \nabla^2 F \\ &- (1 + \nu) L \left( F, \frac{1}{B} \right) + \frac{(1 - \nu^2)}{h} \nabla^2\_k w \\ &= -(1 - \nu) \frac{1}{h} \nabla^2 \left( \frac{N\_T}{B} \right). \end{split} \tag{24}$$

Here T = T(x, y, z) is the temperature field of a general form; α is the coefficient of linear expansion of the material of the blade. ∇<sup>2</sup> and ∇<sup>4</sup> harmonic and biharmonic operators; and ∇<sup>2</sup> *<sup>k</sup>* metaharmonic operator:

∇2 *<sup>k</sup>* ¼ *k*<sup>11</sup> *∂*2 *<sup>∂</sup>x*<sup>2</sup> þ *k*<sup>22</sup> *∂*2 *<sup>∂</sup>y*2; L(D, w) and *L* F, <sup>1</sup> B � � are second-order linear differential operators.

Power factors due to temperature exposure are recorded as:

$$N\_T = \frac{aE}{1-\nu} \int\_{-h/2}^{h/2} T(\mathbf{x}, \mathbf{y}, \mathbf{z}) \, \mathbf{d}\mathbf{z};\\M\_T = \frac{aE}{1-\nu} \int\_{-h/2}^{h/2} T(\mathbf{x}, \mathbf{y}, \mathbf{z}) \, \mathbf{z} \, \mathbf{d}\mathbf{z}.\tag{25}$$

We introduce the dimensionless coordinate system:

$$
\xi = \infty/l; \ \eta = \chi/b\_1; \ m = l/b\_1 \tag{26}
$$

and dimensionless unknown functions

$$
\overline{w} = w/h\_0; \ \overline{F} = \frac{F}{E^\* h\_0^2}.\tag{27}
$$

Here *h*<sup>0</sup> is the characteristic thickness of the scapula and *E*<sup>∗</sup> is the modulus of elasticity of the material of the blade at a temperature of T = 20°C.

The boundary conditions at the edges of the blade adjacent to the disks *η*<sup>1</sup> ¼ *k*1*mξ* þ 1 and *η*<sup>2</sup> ¼ *α*ð Þ *k*1*mξ* þ 1 are considered as follows:

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

$$
\overline{w} = \overline{w}\_{,\mathfrak{n}} = \overline{F} = \overline{F}\_{,\mathfrak{n}} = \mathbf{0}.\tag{28}
$$

The boundary conditions at the inlet and outlet edges of the blade correspond to the free edge. In this case we have:

$$N\_{\xi} = N\_{\xi \eta} = M\_{\xi} = 0; Q\_{\xi} - \frac{\partial M\_{\xi \eta}}{\partial \eta} = 0. \tag{29}$$

The important issue is to specify the function of changing the blade thickness h = h (x, y) in the process of erosion-corrosion wear.

In our studies, the function of changing the blade thickness was set in the form of cubic splines [9].

In the general case, the blade thickness can be represented as two-dimensional spline interpolations:

$$h(\xi\_i, \eta\_i) = h\_0 \sum\_{a=0}^{3} \sum\_{\beta=0}^{3} A\_{a\beta}^{(ij)} (\xi - \xi\_i)^a \left(\eta - \eta\_j\right)^{\beta} (\mathbf{i} = \mathbf{0}, \mathbf{1}, \dots, \mathbf{n}; \mathbf{j} = \mathbf{0}, \mathbf{1}, \dots, \mathbf{m}). \tag{30}$$

This function on each element of the surface of the scapula

$$\begin{bmatrix} \xi\_i, & \xi\_{i+1}; & \eta\_{\mathfrak{j}}, \eta\_{\mathfrak{j}+1} \end{bmatrix}$$

is a bicubic polynomial, continuous, and has continuous partial derivatives up to and including *<sup>∂</sup>*4*h*ð Þ *<sup>ξ</sup>*, *<sup>η</sup> <sup>∂</sup>ξ*2*∂η*<sup>2</sup> , that is *<sup>h</sup>*ð Þ *<sup>ξ</sup>*, *<sup>η</sup>* <sup>∈</sup>*c*2,2.

We represent the system of Eq. (24) in a dimensionless form:

$$\begin{aligned} L\_{11}(\overline{w}) + L\_{12}(\overline{F}) &= L\_{1}; \\ L\_{21}(\overline{w}) + L\_{22}(\overline{F}) &= L\_{2}, \end{aligned} \tag{31}$$

where *Lik*ð Þ *i*, *k* ¼ 1, 2 are dimensionless differential operators of the theory of shells, referred to the lines of curvature of the surface; *Lm* ð Þ m ¼ 1, 2 are components of a given surface and temperature load.

The analytical solution of the system of Eq. (31) with boundary conditions in Eq. (28) is based on the application of the method of integral relations by Dorodnitsyn [13].

In accordance with the method, we write the initial system of Eq. (31) in divergent form:

$$\frac{\partial \overline{X}}{\partial \xi} + \frac{\partial \overline{Y}}{\partial \eta} + \overline{L} = \mathbf{0},\tag{32}$$

where *X* ¼ f g *Xi* ¼ *w*, z1, *z*2, *z*3, *F*, *z*4, *z*5, *z*<sup>6</sup> � �;

$$\overline{Y} = B\_0 \overline{X} + B\_1 \frac{\partial \overline{X}}{\partial \eta} + B\_2 \frac{\partial^2 \overline{X}}{\partial \eta^2} + B\_3 \frac{\partial^3 \overline{X}}{\partial \eta^3}; \overline{L} = B \overline{X} + \overline{b}.$$

Through *z*1, … , z6 marked:

$$z\_1 = \overline{w}\_{,1}; z\_2 = \overline{w}\_{,11}; z\_3 = \overline{w}\_{,111}; z\_4 = \overline{F}\_{,1}; z\_5 = \overline{F}\_{,11}; z\_6 = \overline{F}\_{,111}.$$

In Eq. (32) *Br* ¼ f g *bmn*,*<sup>s</sup>* and *B* ¼ f g *bmn* ;(s = 0, 1, 2, 3; m, n = 1, 2, ..., 8) are transformation matrices.

where x, y are the coordinates of the middle surface of the scapula; T is the temperature; and σ is the function connecting the rate of change of thickness with the stress state at a surface point. Function F should be determined from

Assuming that the rate of change in corrosion wear is a linear function of stress

� �*:* (23)

*<sup>w</sup>* � ð Þ <sup>1</sup> � *<sup>ν</sup> L D*ð Þ� , *<sup>W</sup> <sup>h</sup>*∇<sup>2</sup>

� � are second-order linear differential

*<sup>F</sup>* <sup>þ</sup> <sup>∇</sup><sup>2</sup> <sup>1</sup>

*B* � � ∇2 *F*

*T x*ð Þ , *y*, *z* zdz*:* (25)

*:* (27)

*kF*

*dt* <sup>¼</sup> *<sup>φ</sup>*ð Þ*<sup>t</sup>* <sup>1</sup> <sup>þ</sup> *<sup>k</sup>σij*

*<sup>w</sup>* <sup>þ</sup> <sup>∇</sup><sup>2</sup>

Eq. (23) must be supplemented with shell theory equations of variable thickness. Omitting the intermediate calculations, we present a system of partial differential equations of the type Margherra [14] with respect to the normal deflection w and the stress function F of the eighth order, describing the stress state of the blade

*D*∇<sup>2</sup>

*<sup>F</sup>* <sup>þ</sup> <sup>2</sup> *<sup>∂</sup> ∂y*

Here T = T(x, y, z) is the temperature field of a general form; α is the coefficient

B

1 � *ν*

ð *h=*2

�*h=*2

*E*<sup>∗</sup> *h*<sup>2</sup> 0

*ξ* ¼ *x=l*; *η* ¼ *y=b*1; *m* ¼ *l=b*<sup>1</sup> (26)

*<sup>k</sup>* metaharmonic operator:

of linear expansion of the material of the blade. ∇<sup>2</sup> and ∇<sup>4</sup> harmonic and

*T x*ð Þ , *<sup>y</sup>*, *<sup>z</sup>* dz; *MT* <sup>¼</sup> *<sup>α</sup><sup>E</sup>*

*<sup>w</sup>* <sup>¼</sup> *<sup>w</sup>=h*0; *<sup>F</sup>* <sup>¼</sup> *<sup>F</sup>*

elasticity of the material of the blade at a temperature of T = 20°C.

*k*1*mξ* þ 1 and *η*<sup>2</sup> ¼ *α*ð Þ *k*1*mξ* þ 1 are considered as follows:

Here *h*<sup>0</sup> is the characteristic thickness of the scapula and *E*<sup>∗</sup> is the modulus of

The boundary conditions at the edges of the blade adjacent to the disks *η*<sup>1</sup> ¼

*<sup>∂</sup>y*2; L(D, w) and *L* F, <sup>1</sup>

Power factors due to temperature exposure are recorded as:

1 *B* � � *∂ ∂y* ∇2

*:* (24)

*dh*

of variable thickness, taking into account the temperature effect:

1 *B* � � *∂ ∂x* ∇2

*∂D ∂y ∂ ∂y* ∇2

*∂x*

<sup>1</sup> � *<sup>ν</sup>*<sup>2</sup> ð Þ *<sup>h</sup>* <sup>∇</sup><sup>2</sup> *kw*

*<sup>B</sup>* <sup>∇</sup><sup>4</sup>*<sup>F</sup>* <sup>þ</sup> <sup>2</sup> *<sup>∂</sup>*

þ

*B* � �

*∂*2

ð *h=*2

�*h=*2

and dimensionless unknown functions

We introduce the dimensionless coordinate system:

experiment.

*Corrosion*

*<sup>D</sup>*∇<sup>4</sup>*<sup>w</sup>* <sup>þ</sup> <sup>2</sup>

<sup>¼</sup> *<sup>q</sup>* � <sup>∇</sup><sup>2</sup>

¼ �ð Þ 1 � *ν*

∇2 *<sup>k</sup>* ¼ *k*<sup>11</sup>

operators.

**110**

*∂D ∂x ∂ ∂x* ∇2 *w* þ 2

*MT*; 1

� ð Þ <sup>1</sup> <sup>þ</sup> *<sup>ν</sup> L F*, <sup>1</sup>

1 *<sup>h</sup>* <sup>∇</sup><sup>2</sup> *NT B* � �

biharmonic operators; and ∇<sup>2</sup>

*NT* <sup>¼</sup> *<sup>α</sup><sup>E</sup>* 1 � *ν*

*∂*2 *<sup>∂</sup>x*<sup>2</sup> þ *k*<sup>22</sup>

intensity, we write Eq. (21) in the form:

#### *Corrosion*

Following the method of integral relations of Dorodnitsyn [13], we look for a solution to the system of Eq. (32) in the form of an expansion:

$$X\_{i}(\xi,\eta) = \begin{cases} \sum\_{j=1}^{n} X\_{\vec{\eta}}(\xi)P\_{j}(\xi,\eta) & (\mathbf{i}=\mathbf{3},\mathbf{6},7,\mathbf{8}) \\\\ \sum\_{j=1}^{n} X\_{\vec{\eta}}(\xi)P\_{j,2}(\xi,\eta) & (\mathbf{i}=\mathbf{1},\mathbf{2}) \\\\ \sum\_{j=1}^{n} X\_{\vec{\eta}}(\xi)P\_{j,22}(\xi,\eta) & (\mathbf{i}=\mathbf{4},\mathbf{5}) \end{cases} \tag{33}$$

Here *q* is the degree of the interpolation polynomial and *ak* are coefficients of

þ<sup>X</sup> *q*

where *tm*,*j*,0 ¼ *fm*,*<sup>r</sup>* for *j=r*; *μ* is the number of the fundamental function; and *C<sup>μ</sup>* are integration constants. In solution in Eq. (36), *δ* = 1 if *m = μ* and *δ* = 0 for the

The first approximation *Xm*,*μ*,1 is obtained by substituting the zeroth approxi-

*n* X þ*j*�1

*n* X þ*j*�1

The systems of fundamental functions in Eq. (37) are uniformly converging series, and the coefficients *tm*,*μ*,*n*,*<sup>j</sup>* and *tm*,*n*,*<sup>j</sup>* are determined through the coefficients

*<sup>b</sup>ν*,*m*,*rt<sup>ν</sup>*,*μ*,*n*�1,*j*�*<sup>r</sup>*ð Þ *<sup>n</sup>* <sup>þ</sup> *<sup>j</sup>* � <sup>1</sup> �<sup>1</sup> <sup>Y</sup>*<sup>r</sup>*

*<sup>b</sup><sup>ν</sup>*,*m*,*rt<sup>ν</sup>*,*n*�1,*j*�*<sup>r</sup>*ð Þ *<sup>n</sup>* <sup>þ</sup> *<sup>j</sup>* �<sup>1</sup> <sup>Y</sup>*<sup>r</sup>*

The constants *C<sup>μ</sup>* included in the general solution in Eq. (36) are found from the

*σij* ≤ ½ � *σ<sup>T</sup>* ,

The durability of the impeller element of centrifugal pumps is obtained by

boundary conditions along the inlet and outlet edges of the blade in Eq. (29). Thus, the problem reduces to the joint solution of Eq. (23) and the system of Eq. (24) under initial conditions in Eq. (22) and boundary conditions in Eqs. (28) and (29). Moreover, at each time step, from Eq. (23) we obtain the numerical values of the thickness, which are used to construct spline functions in Eq. (30). Then the system of Eq. (24) is solved, from the solution of which the values *σij* are obtained. The criterion for terminating the step-by-step process is the condition:

*k*¼0

*k*¼0

*akT*<sup>∗</sup>

*akT*<sup>∗</sup> *<sup>k</sup>* ð Þ*ξ* ;

*γ*¼0

*γ*¼0

<sup>0</sup> ð Þ*<sup>ξ</sup> <sup>δ</sup>* into the right-hand side of system *dXm*

Subsequent approximations are carried out according to the formulas:

*j*¼0

The general solution of the system of Eq. (34) has the form [10, 19, 20]:

*Xm*,*μ*,*<sup>n</sup>*

*<sup>k</sup>* ð Þ*ξ* . In expressions of

*j*þ1

*akT*<sup>∗</sup> *<sup>k</sup>* ð Þ*ξ*

(36)

(37)

*k*¼0

*Bν*,*mXν*.

*tm*,*j*,0 *<sup>d</sup> <sup>j</sup>*þ1ð Þ *<sup>j</sup>* <sup>þ</sup> <sup>1</sup> ! � ��1<sup>X</sup>

*<sup>d</sup><sup>ξ</sup>* <sup>¼</sup> <sup>P</sup>*<sup>s</sup> ν*¼1

*<sup>k</sup>* ð Þ*ξ* , where *β* ¼ *n q*ð ÞÞ þ 3 –2

ð Þ *n* þ *j* � 1 � *γ* ,

ð Þ *n* þ *j* � *γ :*

expansion of *ξ<sup>r</sup>* in a series of Chebyshev polynomials *T*<sup>∗</sup>

*Xm* <sup>¼</sup> <sup>X</sup>*<sup>s</sup>*

remaining *μ*.

mation: *d*�<sup>1</sup>

*μ*¼1

þX<sup>∞</sup> *n*¼2

<sup>0</sup> *a*0*T*<sup>∗</sup>

*β*

*j*¼1

*j*¼1

*tm*,*μ*,*n*,*<sup>j</sup>* <sup>¼</sup> <sup>X</sup>*<sup>s</sup>*

*ν*¼1

*tm*,*n*,*<sup>j</sup>* <sup>¼</sup> <sup>X</sup>*<sup>s</sup>*

X *q*

*r*¼0

*ν*¼1

where *σ<sup>T</sup>* is the yield strength of the material.

summing the steps in time.

**113**

*Xm*,*μ*,*<sup>n</sup>* <sup>¼</sup> <sup>X</sup>

*Xm*,*<sup>n</sup>* <sup>¼</sup> <sup>X</sup> *β*

*C<sup>μ</sup> d*�<sup>1</sup>

*Xm*,*n*,

<sup>0</sup> *a*0*T* <sup>∗</sup>

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

Eq. (35), *dr* <sup>¼</sup> 1 for *<sup>r</sup>* = 0 and *dr* <sup>¼</sup> 22*<sup>r</sup>*�<sup>1</sup> for the remaining *<sup>r</sup>*.

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

<sup>0</sup> ð Þ*<sup>ξ</sup> <sup>δ</sup>* <sup>þ</sup>X<sup>∞</sup>

*tm*,*μ*,*n*,*<sup>j</sup> dn*þ*j*�<sup>1</sup>ð Þ *<sup>n</sup>* <sup>þ</sup> *<sup>j</sup>* � <sup>1</sup> ! � ��<sup>1</sup>

*tm*,*n*,*<sup>j</sup> dn*þ*j*�<sup>1</sup>ð Þ *<sup>n</sup>* <sup>þ</sup> *<sup>j</sup>* � <sup>1</sup> ! � ��<sup>1</sup>

of the previous approximation using recurrence formulas:

X *q*

*r*¼0

" #

*n*¼1

As approximating and weighting functions, we choose the Jacobi system of orthogonal polynomials [15, 16] and their derivatives:

$$P\_j(\xi,\eta) = P\_1(\xi,\eta) \sum\_{j=1}^n \left[\eta - \frac{(1+a)r}{2}\right]^{j-1};$$

$$P\_1(\xi,\eta) = \eta^4 - 2(1+a)r\eta^3 + \left(1+4a+a^2\right)r^2\eta^2 - 2a(1+a)r^3\eta + a^2r^4.$$

Here*r* ¼ 1 þ *k*1*mξ* is the equation of the inclined side of the scapula.

Note that polynomials *P <sup>j</sup>*ð Þ *ξ*, *η* are orthogonal on the interval [*η*1, *η*2] and forming a system of linearly independent functions, they satisfy the boundary conditions at the oblique edges of the blade in Eq. (28).

We also emphasize that their derivatives Pj,2ð Þ *ξ*, *η* and *P <sup>j</sup>*,22ð Þ *ξ*, *η* also have the property of orthogonality.

Restricting ourselves to the two-term approximation and also choosing power polynomials *P <sup>j</sup>*ð Þ *ξ*, *η* and their derivatives as weight functions, after applying the procedure of the method of integral relations to the original system of Eq. (32), we obtain a system of ordinary differential equations of order 8n with variable coefficients:

$$\frac{dX\_m}{d\xi} = \sum\_{\nu=1}^s B\_{\nu,m} X\_{\nu} + f\_m, \quad m = 1, 2, \dots, s \tag{34}$$

It should be noted that in the general case there is no exact solution of such equations in mathematics, with the exception of individual special cases, for example, the Bessel equation.

Here, the modified method of successive approximations developed by Professor Pukhliy and published by him in the Academic Press [12, 17] is applied to the solution of the boundary-value problem.

Later, the method was extended to the solution of initial-boundary value problems [4], and to accelerate the convergence of the solution, the method of telescopic shift of the power series of K. Lanczos [18] was used. For this, we used the possibility of representing any power series in terms of shifted Chebyshev polynomials [15, 16]. For the first time, such an approach was presented in the works of V.A. Pukhliy [19, 20].

In accordance with the method, variable coefficients *B<sup>ν</sup>*,*<sup>m</sup>* and free terms *fm* can be represented through shifted Chebyshev polynomials:

$$f\_m = \sum\_{r=0}^q f\_{m,r} (d\_r \cdot r!)^{-1} \sum\_{k=0}^r a\_k T\_k^\* \left(\xi\right), \quad B\_{\nu,m} = \sum\_{r=0}^q b\_{\nu,m,r} d\_r^{-1} \sum\_{k=0}^r a\_k T\_k^\* \left(\xi\right) \tag{35}$$

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

Here *q* is the degree of the interpolation polynomial and *ak* are coefficients of expansion of *ξ<sup>r</sup>* in a series of Chebyshev polynomials *T*<sup>∗</sup> *<sup>k</sup>* ð Þ*ξ* . In expressions of Eq. (35), *dr* <sup>¼</sup> 1 for *<sup>r</sup>* = 0 and *dr* <sup>¼</sup> 22*<sup>r</sup>*�<sup>1</sup> for the remaining *<sup>r</sup>*.

The general solution of the system of Eq. (34) has the form [10, 19, 20]:

$$\begin{split} X\_m &= \sum\_{\mu=1}^s C\_{\mu} \left[ d\_0^{-1} a\_0 T\_0^\* \left( \xi \right) \delta + \sum\_{n=1}^\infty X\_{m,\mu,\mathfrak{a}} \right] + \sum\_{j=0}^q t\_{mj,0} \left[ d\_{j+1} (\not{j} + \mathbf{1})! \right]^{-1} \sum\_{k=0}^{j+1} a\_k T\_k^\* \left( \xi \right) \\ &+ \sum\_{n=2}^\infty X\_{m,n}, \end{split} \tag{36}$$

where *tm*,*j*,0 ¼ *fm*,*<sup>r</sup>* for *j=r*; *μ* is the number of the fundamental function; and *C<sup>μ</sup>* are integration constants. In solution in Eq. (36), *δ* = 1 if *m = μ* and *δ* = 0 for the remaining *μ*.

The first approximation *Xm*,*μ*,1 is obtained by substituting the zeroth approximation: *d*�<sup>1</sup> <sup>0</sup> *a*0*T*<sup>∗</sup> <sup>0</sup> ð Þ*<sup>ξ</sup> <sup>δ</sup>* into the right-hand side of system *dXm <sup>d</sup><sup>ξ</sup>* <sup>¼</sup> <sup>P</sup>*<sup>s</sup> ν*¼1 *Bν*,*mXν*.

Subsequent approximations are carried out according to the formulas:

$$X\_{m,n,n} = \sum\_{j=1}^{\beta} t\_{m,n,j} \left[ d\_{n+j-1} (n+j-1)! \right]^{-1} \sum\_{k=0}^{n+j-1} a\_k T\_k^\* \left( \xi \right);$$

$$X\_{m,n} = \sum\_{j=1}^{\beta} t\_{m,n,j} \left[ d\_{n+j-1} (n+j-1)! \right]^{-1} \sum\_{k=0}^{n+j-1} a\_k T\_k^\* \left( \xi \right), \text{ where } \beta = n(q+3) \text{ (} -2 \text{)} \tag{37}$$

The systems of fundamental functions in Eq. (37) are uniformly converging series, and the coefficients *tm*,*μ*,*n*,*<sup>j</sup>* and *tm*,*n*,*<sup>j</sup>* are determined through the coefficients of the previous approximation using recurrence formulas:

$$t\_{m,\mu,n,j} = \sum\_{\nu=1}^{s} \sum\_{r=0}^{q} b\_{\nu,m,r} t\_{\nu,\mu,n-1,j-r} (n+j-1)^{-1} \prod\_{\gamma=0}^{r} (n+j-1-\gamma),$$

$$t\_{m,n,j} = \sum\_{\nu=1}^{s} \sum\_{r=0}^{q} b\_{\nu,m,r} t\_{\nu,n-1,j-r} (n+j)^{-1} \prod\_{\gamma=0}^{r} (n+j-\gamma).$$

The constants *C<sup>μ</sup>* included in the general solution in Eq. (36) are found from the boundary conditions along the inlet and outlet edges of the blade in Eq. (29).

Thus, the problem reduces to the joint solution of Eq. (23) and the system of Eq. (24) under initial conditions in Eq. (22) and boundary conditions in Eqs. (28) and (29). Moreover, at each time step, from Eq. (23) we obtain the numerical values of the thickness, which are used to construct spline functions in Eq. (30). Then the system of Eq. (24) is solved, from the solution of which the values *σij* are obtained.

The criterion for terminating the step-by-step process is the condition:

$$
\sigma\_{\vec{\eta}} \le [\sigma\_T],
$$

where *σ<sup>T</sup>* is the yield strength of the material.

The durability of the impeller element of centrifugal pumps is obtained by summing the steps in time.

Following the method of integral relations of Dorodnitsyn [13], we look for a

As approximating and weighting functions, we choose the Jacobi system of

*j*¼1

We also emphasize that their derivatives Pj,2ð Þ *ξ*, *η* and *P <sup>j</sup>*,22ð Þ *ξ*, *η* also have the

Restricting ourselves to the two-term approximation and also choosing power polynomials *P <sup>j</sup>*ð Þ *ξ*, *η* and their derivatives as weight functions, after applying the procedure of the method of integral relations to the original system of Eq. (32), we obtain a system of ordinary differential equations of order 8n with variable

It should be noted that in the general case there is no exact solution of such equations in mathematics, with the exception of individual special cases, for exam-

Here, the modified method of successive approximations developed by Professor Pukhliy and published by him in the Academic Press [12, 17] is applied to the

Later, the method was extended to the solution of initial-boundary value problems [4], and to accelerate the convergence of the solution, the method of telescopic shift of the power series of K. Lanczos [18] was used. For this, we used the possibility of representing any power series in terms of shifted Chebyshev polynomials [15, 16]. For the first time, such an approach was presented in the works of V.A.

In accordance with the method, variable coefficients *B<sup>ν</sup>*,*<sup>m</sup>* and free terms *fm* can

*<sup>k</sup>* ð Þ*<sup>ξ</sup>* , *<sup>B</sup><sup>ν</sup>*,*<sup>m</sup>* <sup>¼</sup> <sup>X</sup>

*q*

*bν*,*m*,*rd*�<sup>1</sup> *r* X*r k*¼0

*akT* <sup>∗</sup>

*<sup>k</sup>* ð Þ*ξ* (35)

*r*¼0

Here*r* ¼ 1 þ *k*1*mξ* is the equation of the inclined side of the scapula. Note that polynomials *P <sup>j</sup>*ð Þ *ξ*, *η* are orthogonal on the interval [*η*1, *η*2] and forming a system of linearly independent functions, they satisfy the boundary

*Xij*ð Þ*ξ P <sup>j</sup>*ð Þ *ξ*, *η* ð Þ i ¼ 3, 6, 7, 8

*Xij*ð Þ*ξ P <sup>j</sup>*,2ð Þ *ξ*, *η* ð Þ i ¼ 1, 2

(33)

*Xij*ð Þ*ξ P <sup>j</sup>*,22ð Þ *ξ*, *η* ð Þ i ¼ 4, 5

*<sup>η</sup>* � ð Þ <sup>1</sup> <sup>þ</sup> *<sup>α</sup> <sup>r</sup>* 2 � � *<sup>j</sup>*�<sup>1</sup>

2

;

3 *<sup>η</sup>* <sup>þ</sup> *<sup>α</sup>*<sup>2</sup> *r* 4*:*

*<sup>η</sup>*<sup>2</sup> � <sup>2</sup>*α*ð Þ <sup>1</sup> <sup>þ</sup> *<sup>α</sup> <sup>r</sup>*

*Bν*,*mX<sup>ν</sup>* þ *fm*, m ¼ 1, 2, … , s (34)

solution to the system of Eq. (32) in the form of an expansion:

P*n j*¼1

8

>>>>>>>>><

>>>>>>>>>:

orthogonal polynomials [15, 16] and their derivatives:

P*n j*¼1

P*n j*¼1

*<sup>P</sup> <sup>j</sup>*ð Þ¼ *<sup>ξ</sup>*, *<sup>η</sup> <sup>P</sup>*1ð Þ *<sup>ξ</sup>*, *<sup>η</sup>* <sup>X</sup>*<sup>n</sup>*

*<sup>P</sup>*1ð Þ¼ *<sup>ξ</sup>*, *<sup>η</sup> <sup>η</sup>*<sup>4</sup> � 2 1ð Þ <sup>þ</sup> *<sup>α</sup> <sup>r</sup>η*<sup>3</sup> <sup>þ</sup> <sup>1</sup> <sup>þ</sup> <sup>4</sup>*<sup>α</sup>* <sup>þ</sup> *<sup>α</sup>*<sup>2</sup> � �*<sup>r</sup>*

conditions at the oblique edges of the blade in Eq. (28).

*dXm <sup>d</sup><sup>ξ</sup>* <sup>¼</sup> <sup>X</sup>*<sup>s</sup> ν*¼1

solution of the boundary-value problem.

*fm*,*<sup>r</sup> dr* ð Þ � *<sup>r</sup>*! �<sup>1</sup>X*<sup>r</sup>*

be represented through shifted Chebyshev polynomials:

*k*¼0

*akT*<sup>∗</sup>

property of orthogonality.

ple, the Bessel equation.

Pukhliy [19, 20].

*fm* <sup>¼</sup> <sup>X</sup> *q*

**112**

*r*¼0

coefficients:

*Corrosion*

*Xi*ð Þ¼ *ξ*, *η*

#### **4. Conclusions**

The theory of corrosion wear of structural elements of hydropower and nuclear energy in the form of plates and shells is developed taking into account the stress state and corrosion wear.

**References**

[1] Pukhliy VA, Semenenko VI, Zhuzhman VY. New in anti-corrosion protection of elements of industrial ventilation systems. In: Theses of the report on Vses. Scientific and Technical Conf. "Corrosion protection and environmental protection." M.; 1980

*DOI: http://dx.doi.org/10.5772/intechopen.92188*

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State*

corrosive environment. In: Selected Works "Problems of the Mechanics of a Deformable Solid". M.: Publishing House "Science"; 1991. pp. 75-80

[9] Alberg J, Nielson E, Walsh J. Theory of Splines and its Applications. M.: Mir Publishing House; 1972. pp. 318

mathematical physics by the modified method of successive approximations. Review of Applied and Industrial Mathematics. 2017;**24**(1):37-48

[11] Pukhliy VA, Miroshnichenko ST, Zhuravlev AA. Thermoelasticity of the blades of centrifugal pumps of nuclear power under the influence of hightemperature and radiation fields. In: Proceedings of the 12th All-Russian Congress on Fundamental Problems of Theoretical and Applied Mechanics; Vol. 3. Ufa: RAS; 2019. pp. 1203-1205

[12] Pukhliy VA. A method for the analytical solution of two-dimensional boundary value problems for systems of elliptic equations. USSR Computational Mathematics and Mathematical Physics.

[13] Dorodnitsyn AA. On a method for solving the equations of a laminar boundary layer. Journal. Adj. Mate. and

Tech. Physics. 1960;**3**:111-118

[14] Marguerre K. Zur theorie der gekrümmten Platte großer

Formänderung. In: Jahrbuch 1939 der deutschen Luftfahrforschung. Vol. i.

[15] Courant R, Hilbert D. Methods of Mathematical Physics. Vol. I. M.:

[16] Luke VL. Mathematical Functions and Their Approximations. New York,

1978;**18**(5):1275-1282

1939. pp. 413-418

Gostekhizdat; 1953

[10] Pukhliy VA. Solving initial boundary value problems of

[2] Kornishin MS, Karpunin VG, Kleschev SI. To the calculation of plates and shells, taking into account general corrosion. In: Proceedings of X All. Conference on the Theory of Shells and Plates. Vol. 2. Tbilisi: Metsnireba Publishing House; 1975. pp. 71-78

[3] Ovchinnikov IG, Sabitov HA. A comparative study of the extrapolation capabilities of some models of corrosion wear on the example of the calculation of a cylindrical shell. Proceedings of Universities. Construction and Architecture. 1986;**1**:42-45

[4] Pukhliy VA, Nusuev VN,

[6] Matveenko AF, Baldin AV,

[7] Matvienko AF, Baldin AV,

24-31

**115**

Semenenko VI. Corrosion-resistant fans with a polymer protective coating. In: Improving the Efficiency of Fan Installations. M.; 1982. pp. 111-116

[5] Pukhliy VA. To the theory of erosioncorrosion wear. In: Questions of the Aerodynamics of Textile Equipment. M.: VNIIL Tekmash; 1988. pp. 122-135

Grigoriev AP. Stress corrosion cracking of steels of main gas pipelines. I. Emergency destruction. Physics of Metals and Metallurgy. 1998;**86**(2):

Grigoriev AP. Stress corrosion cracking of steels of main gas pipelines. II. On the relationship of mechanical properties and resistance of SCC. Metal Physics Metallurgy. 1998;**86**(2):147-155

[8] Rabotnov YN. About a possible mechanism of metal destruction in a

Numerous factors affecting the speed of the corrosion wear process (degree of aggressiveness of the media, temperature, humidity, etc.) are taken into account in a generalized way by drawing up a differential equation for the rate of change of the thickness of the impeller element.

The criterion for the ultimate state of structural elements is the achievement by the structural element of the yield strength of the material *σT*.

An algorithm has been developed for solving the problem of corrosion wear of bimetallic pipelines of nuclear energy, taking into account the stress-strain state of the elements.

An algorithm has been developed for the analytical solution of the problem of corrosion wear of rotor blades of centrifugal pumps based on a combination of the method of integral relations and the modified method of successive approximations in displaced Chebyshev polynomials.

#### **Acknowledgements**

Research has been funded by RFBR and City of Sevastopol under Research Project №18-48-920002.

#### **Author details**

Vladimir A. Pukhliy Sevastopol State University, Sevastopol, Russia

\*Address all correspondence to: pu1611@rambler.ru

© 2020 The Author(s). Licensee IntechOpen. This chapter is distributed under the terms of the Creative Commons Attribution License (http://creativecommons.org/licenses/ by/3.0), which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

*Corrosion Wear of Pipelines and Equipment in Complex Stress-Strain State DOI: http://dx.doi.org/10.5772/intechopen.92188*

#### **References**

**4. Conclusions**

*Corrosion*

the elements.

state and corrosion wear.

thickness of the impeller element.

in displaced Chebyshev polynomials.

**Acknowledgements**

Project №18-48-920002.

**Author details**

**114**

Vladimir A. Pukhliy

Sevastopol State University, Sevastopol, Russia

provided the original work is properly cited.

\*Address all correspondence to: pu1611@rambler.ru

The theory of corrosion wear of structural elements of hydropower and nuclear energy in the form of plates and shells is developed taking into account the stress

Numerous factors affecting the speed of the corrosion wear process (degree of aggressiveness of the media, temperature, humidity, etc.) are taken into account in a generalized way by drawing up a differential equation for the rate of change of the

The criterion for the ultimate state of structural elements is the achievement by

An algorithm has been developed for solving the problem of corrosion wear of bimetallic pipelines of nuclear energy, taking into account the stress-strain state of

An algorithm has been developed for the analytical solution of the problem of corrosion wear of rotor blades of centrifugal pumps based on a combination of the method of integral relations and the modified method of successive approximations

Research has been funded by RFBR and City of Sevastopol under Research

© 2020 The Author(s). Licensee IntechOpen. This chapter is distributed under the terms of the Creative Commons Attribution License (http://creativecommons.org/licenses/ by/3.0), which permits unrestricted use, distribution, and reproduction in any medium,

the structural element of the yield strength of the material *σT*.

[1] Pukhliy VA, Semenenko VI, Zhuzhman VY. New in anti-corrosion protection of elements of industrial ventilation systems. In: Theses of the report on Vses. Scientific and Technical Conf. "Corrosion protection and environmental protection." M.; 1980

[2] Kornishin MS, Karpunin VG, Kleschev SI. To the calculation of plates and shells, taking into account general corrosion. In: Proceedings of X All. Conference on the Theory of Shells and Plates. Vol. 2. Tbilisi: Metsnireba Publishing House; 1975. pp. 71-78

[3] Ovchinnikov IG, Sabitov HA. A comparative study of the extrapolation capabilities of some models of corrosion wear on the example of the calculation of a cylindrical shell. Proceedings of Universities. Construction and Architecture. 1986;**1**:42-45

[4] Pukhliy VA, Nusuev VN, Semenenko VI. Corrosion-resistant fans with a polymer protective coating. In: Improving the Efficiency of Fan Installations. M.; 1982. pp. 111-116

[5] Pukhliy VA. To the theory of erosioncorrosion wear. In: Questions of the Aerodynamics of Textile Equipment. M.: VNIIL Tekmash; 1988. pp. 122-135

[6] Matveenko AF, Baldin AV, Grigoriev AP. Stress corrosion cracking of steels of main gas pipelines. I. Emergency destruction. Physics of Metals and Metallurgy. 1998;**86**(2): 24-31

[7] Matvienko AF, Baldin AV, Grigoriev AP. Stress corrosion cracking of steels of main gas pipelines. II. On the relationship of mechanical properties and resistance of SCC. Metal Physics Metallurgy. 1998;**86**(2):147-155

[8] Rabotnov YN. About a possible mechanism of metal destruction in a corrosive environment. In: Selected Works "Problems of the Mechanics of a Deformable Solid". M.: Publishing House "Science"; 1991. pp. 75-80

[9] Alberg J, Nielson E, Walsh J. Theory of Splines and its Applications. M.: Mir Publishing House; 1972. pp. 318

[10] Pukhliy VA. Solving initial boundary value problems of mathematical physics by the modified method of successive approximations. Review of Applied and Industrial Mathematics. 2017;**24**(1):37-48

[11] Pukhliy VA, Miroshnichenko ST, Zhuravlev AA. Thermoelasticity of the blades of centrifugal pumps of nuclear power under the influence of hightemperature and radiation fields. In: Proceedings of the 12th All-Russian Congress on Fundamental Problems of Theoretical and Applied Mechanics; Vol. 3. Ufa: RAS; 2019. pp. 1203-1205

[12] Pukhliy VA. A method for the analytical solution of two-dimensional boundary value problems for systems of elliptic equations. USSR Computational Mathematics and Mathematical Physics. 1978;**18**(5):1275-1282

[13] Dorodnitsyn AA. On a method for solving the equations of a laminar boundary layer. Journal. Adj. Mate. and Tech. Physics. 1960;**3**:111-118

[14] Marguerre K. Zur theorie der gekrümmten Platte großer Formänderung. In: Jahrbuch 1939 der deutschen Luftfahrforschung. Vol. i. 1939. pp. 413-418

[15] Courant R, Hilbert D. Methods of Mathematical Physics. Vol. I. M.: Gostekhizdat; 1953

[16] Luke VL. Mathematical Functions and Their Approximations. New York, London: Academic Press. Inc.; 1975. pp. 608

[17] Pukhliy VA. About one approach to solving boundary value problems of mathematical physics. Differential Equations. 1979;**15**(11):2039-2043

[18] Lantsosh K. Practical Methods of Applied Analysis. M.: Fizmatgiz; 1961. pp. 524

[19] Pukhliy VA. The solution to the problem of bending oblique in terms of a cylindrical three-layer panel by the modified method of successive approximations. Applied Mechanics. 1986;**22**(10):62-67

[20] Pukhliy VA. An analytical method for solving boundary value problems of shell theory. In: Proceedings of the XIII All-Union. Conference on the Theory of Plates and Shells. Part IV-Tallinn. TPI Publishing House; 1983. pp. 101-107

**117**

**Chapter 7**

**Abstract**

material.

**1. Introduction**

Spectroscopy in Oilfield Corrosion

Interaction of surfaces of metals and alloys with electromagnetic radiation produces several interesting phenomena, including electronic transitions, molecular rotation and vibration within bonds, polarisation, or photochemical reactions. Spectroscopy is an essential tool that provides some structural information about these interactions. In corrosion, spectroscopic techniques are often employed for mechanistic determinations, especially in the presence of corrosion inhibitors. In this chapter, we have examined some spectroscopic methods that are useful for corrosion monitoring and corrosion inhibition. More emphasis is placed on sample preparation, output parameters, interpretation of results and possible deductions/predictions, which could be made from obtained results than on the underlying principles and mode of equipment operation. Attempts are also made to critically examine some literature, hence readers (early career researchers) and experts in the field will find this chapter very resourceful and a ready reference

Once existing wells begin to deplete, it becomes essential to use some principles of chemistry and materials science to maintain production through operations, such as well acidising, secondary and enhanced oil recovery. A common field technique for achieving this is to force a fluid (mixtures which could include acid, water and polymers) through the well bore at high pressure. This fluid dissolves formation rocks, enlarges existing flow channels and opens new ones by etching to enhance the flow of hydrocarbons. During this procedure, corrosion of steel structural materials often occurs. Such materials include line pipes, casings and tubings. After recovery, the spent acid could also cause corrosion of storage facilities. Problems associated with such corrosion could include rupturing of materials, spills, failure, loss of hydrocarbons and loss of materials' integrity and flow challenges. The cost of maintaining/cleaning spills is often high, hence most industries would find methods to prevent or retard corrosion. Also, the downtime due to the shutdown of plant for maintenance and damage to employees or company integrity is undesirable. The use of corrosion inhibitors (CIs) has been considered the simplest and cost-effective means of mitigating oilfield corrosion. Corrosion inhibitors (CIs) are chemical

Monitoring and Inhibition

*Ekemini Ituen, Lin Yuanhua, Ambrish Singh* 

**Keywords:** corrosion products, EDS, EIS, FTIR, UV-Vis, XRD

*and Onyewuchi Akaranta*

#### **Chapter 7**

London: Academic Press. Inc.; 1975.

[17] Pukhliy VA. About one approach to solving boundary value problems of mathematical physics. Differential Equations. 1979;**15**(11):2039-2043

[18] Lantsosh K. Practical Methods of Applied Analysis. M.: Fizmatgiz; 1961.

[19] Pukhliy VA. The solution to the problem of bending oblique in terms of a cylindrical three-layer panel by the modified method of successive approximations. Applied Mechanics.

[20] Pukhliy VA. An analytical method for solving boundary value problems of shell theory. In: Proceedings of the XIII All-Union. Conference on the Theory of Plates and Shells. Part IV-Tallinn. TPI Publishing House; 1983. pp. 101-107

pp. 608

*Corrosion*

pp. 524

**116**

1986;**22**(10):62-67
